EP3538753B1 - Control device for an internal combustion engine - Google Patents

Control device for an internal combustion engine Download PDF

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Publication number
EP3538753B1
EP3538753B1 EP17793661.4A EP17793661A EP3538753B1 EP 3538753 B1 EP3538753 B1 EP 3538753B1 EP 17793661 A EP17793661 A EP 17793661A EP 3538753 B1 EP3538753 B1 EP 3538753B1
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EP
European Patent Office
Prior art keywords
channel
internal combustion
combustion engine
control device
valve seat
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EP17793661.4A
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German (de)
French (fr)
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EP3538753A1 (en
Inventor
Thorsten REIMERS
Patrick SUTTY
Dirk VIERKOTTEN
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Pierburg GmbH
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Pierburg GmbH
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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
    • F02M26/52—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
    • 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
    • F02M26/71—Multi-way valves
    • 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
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
    • F02M35/10222—Exhaust gas recirculation [EGR]; Positive crankcase ventilation [PCV]; Additional air admission, lubricant or fuel vapour admission
    • 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

Definitions

  • the invention relates to a control device for an internal combustion engine with an intake channel, an exhaust gas recirculation channel that opens into the intake channel, a housing in which the intake channel and at least one mouth of the exhaust gas recirculation channel are formed, a shaft serving as a rotation axis, which is upstream in the housing with respect to the air flow the mouth of the exhaust gas recirculation duct and outside the flow cross-section and is arranged perpendicular to the central axes of the intake duct and the exhaust gas recirculation duct, a regulating body which is eccentrically attached to the shaft, a first duct section in a first housing part, at the downstream end of which a first valve seat is formed against which the regulating body rests in a first end position, and the outer circumference of which is smaller than the outer circumference of a downstream second duct section and a second valve seat on the second duct section on which the regulating body in a second end position, in which the control body closes the exhaust gas recirculation duct.
  • Control devices are used in internal combustion engines to regulate the amount of exhaust gas or air that is to be discharged or fed to combustion. Combinations of these control valves, in which two valve bodies are actuated via a common adjusting device, are also known.
  • combinations of an exhaust gas recirculation valve with a throttle valve have been disclosed.
  • the exhaust gas recirculation channel opens into the air intake channel immediately downstream of the flap serving as a throttle valve.
  • the throttle valve is closed to the same extent when the exhaust gas recirculation valve is opened, which increases the pressure drop 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 27 03 687 A1 disclosed.
  • a regulating device is also known in which two flaps arranged in parallel are actuated via a common eccentrically arranged rotating shaft, so that when the two flaps rotate, the first flap moves away from the valve seat of the air intake duct, while the second flap approaches the valve seat of the exhaust gas recirculation duct until the Air intake duct is fully open and the exhaust gas recirculation duct is completely closed.
  • the valve seats are each designed as circumferential 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 channel and the valve seat in the air intake channel, but is arranged outside the flow cross section of the upstream channel section.
  • the formation of condensate in the mixed gas flow downstream of the exhaust gas recirculation duct should be excluded as far as possible in order to prevent damage to a downstream compressor.
  • the shape of a surface of the control body facing the inside of the intake channel in the second end position corresponds in a cross section perpendicular to the central axis of the first housing part over an angle of at least 90 ° to an inner wall surface of the first channel section adjoining the control body, the first channel section becomes over a circumferential section is extended essentially without interference, as a result of which eddies in the area of the exhaust gas inlet or on the outside of the regulating body are prevented, so that a significant reduction in pressure losses is achieved.
  • the mixing of the warm exhaust gas flow with the cold air flow is delayed by this flow guidance, whereby the amount of condensate is reduced, so that a downstream compressor is protected from damage by liquid water.
  • the shape of the surface of the regulating body facing the inside of the intake duct corresponds in a cross section perpendicular to the central axis over half a circumference of the inner wall surface of the first duct section adjoining the regulating body.
  • the regulating body extends in the second end position up to a third duct section, the inner circumference of which is smaller than the inner circumference of the second duct section, so that a continuous course without cross-sectional jumps between the second and third duct sections in the regulating body releasing the intake duct can be produced. In this way, the pressure loss can also be kept low in this area.
  • the first valve seat is formed by an axial end of a first housing part of the housing which forms the first channel section and protrudes into a second housing part of the housing which forms at least the second channel section.
  • the valve seat can be machined in a simple manner before assembly.
  • a full-surface support of the control body on the first valve seat to close the intake channel is easy to produce, since the first housing part is in the second protrudes and thus provides an axial contact surface which enables a tight seal.
  • the first housing part is connected to the second housing part via a flange. This enables simple assembly with a high level of tightness between the housing parts.
  • the regulating body In its first end position, the regulating body preferably lies completely circumferentially against the first valve seat at the end of the first housing part. This enables a tight closure of the intake channel through the axial contact. As a result, a large closing force of the control body also acts on the valve seat, since the component acting in the axial direction of the force resulting from the applied torque is large. This means that smaller actuators can be used.
  • the central axis of the first channel section runs parallel to the central axis of the third channel section. In this way, a flow guide can be produced without steps and deflections, whereby the flow resistance is kept low.
  • a first plane spanned by the first valve seat is arranged at an angle of 75 ° to 80 ° to a second plane spanned by the second valve seat.
  • the first plane forms an acute angle to a plane which is arranged perpendicular to the central axis of the intake duct
  • the second plane forms an acute angle Angle to a plane which is arranged perpendicular to the central axis of the exhaust gas recirculation duct.
  • the valve seat surfaces are inclined to one another in comparison to the channel center axes, so that the adjustment paths are short and enable rapid regulation.
  • the control body preferably has a first flap part, on which the surface is formed, which rests against the first valve seat in the first end position, and a second flap part which rests against the second valve seat in the second end position, the two flap parts via a Intermediate element are connected to the shaft.
  • the second flap part consists, for example, of a holding shaft which is received in a tiltable manner in a bore of the intermediate element and a flat flap body attached to it. This simplifies the manufacture of the control body.
  • 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 duct can be regulated quickly and precisely over a large adjustment angle range, with existing pressure losses being minimized by avoiding flow obstacles and dead spaces in which undesirable eddies could form be reduced. Instead, a largely uniform flow is generated without any changes in cross-section.
  • the reduced eddy formation also improves the flow to a downstream compressor and prevents damage to the compressor by reducing the amount of condensate that accumulates through better separation of the exhaust gas flow from the air flow.
  • the Figure 1 shows a side view of a control device according to the invention with a control body in a first end position in a sectional view.
  • the Figure 2 shows a side view of the control device according to the invention Figure 1 with a control body in a second end position in a sectional view.
  • the Figure 3 shows a top view of the control device according to the invention from Figure 2 with a control body in the second end position in a sectional view.
  • the control device consists of a housing 10 which delimits an intake duct 12 and in which an opening 14 of an exhaust gas recirculation duct 16 is formed.
  • the intake channel 12 runs essentially in a straight direction, while the exhaust gas recirculation channel 16 opens into the intake channel 12 perpendicular to the latter.
  • the housing 10 consists of a first, essentially tubular housing part 18, which forms a first channel section 19 and the downstream end of which is inclined and includes an angle ⁇ of approximately 75 ° to a central axis 20 of the housing part 18.
  • the downstream end of the first housing part 18 is arranged in the interior of a second housing part 22, or is pushed into the second housing part 22 until a flange 24 abuts, via which the first housing part 18 is fastened to the second housing part 22 by means of screws 26.
  • the second housing part 22 forms a second channel section 28 in which an opening 30 is formed, which is arranged in the flow direction at a short distance behind the inclined end of the first housing part 18 and which serves as a receptacle for a third housing part 32, which the mouth 14 of the Forms exhaust gas recirculation duct 16, the central axis 34 of which is arranged perpendicular to the central axis 20 of the intake duct 12,
  • a shaft 36 is rotatably arranged in the housing 10 and can be actuated via an actuator which is not visible.
  • the axis of rotation 38 of this shaft 36 is arranged perpendicular to the central axes 20, 34 and is located between the mouth 14 of the exhaust gas recirculation duct 16 downstream of the shaft 36 and the axial end of the first housing part 18 and immediately downstream of the first housing part 18.
  • the overall cross section of the first housing part 18 is smaller than that of the second housing part 22 of the intake duct 12, the first housing part 18 being fastened to the second housing part 22 in such a way that a recess 40 formed in the region of the mouth 14 of the exhaust gas recirculation duct 16 is arranged outside the flow cross-section in which the shaft 36 the second housing part 22 is arranged penetrating.
  • a regulating body 42 is attached to this eccentrically arranged shaft 36 in the intake channel 12, which is arranged rotatably within the second channel section 28 and consists of a first flap part 44 and a second flap part 45, which has a holding axis 46 and a flap body 48 attached to it such that it can tilt, wherein the holding shaft 46 is mounted in a bore of an intermediate element 49 such that it can tilt.
  • the intermediate element 49 is either produced in one piece with the first flap part 44 or connected to it and has a connection to the shaft 36.
  • the first flap part 44 When the shaft 36 is rotated, the first flap part 44 is rotated in a first end position against the end of the first housing part 18, which accordingly serves as the first valve seat 50, while when rotated in the opposite direction, the flap body 48 is in a second end position against one end of the mouth 14 of the exhaust gas recirculation duct 16, which serves as a second valve seat 52, is rotated.
  • the Exhaust gas recirculation duct 16 is closed by the flap body 48 and vice versa.
  • the tiltable fastening of the second flap part 45 leads to this rotational movement of the shaft 36 in a second end position, in which the flap body 48 rests on the second valve seat 52, that a completely tight closure of the exhaust gas recirculation channel 16 takes place, since the flap body 48 is in its position can adapt the possible tilting movement to the position of the second valve seat 52, even if it is not completely in alignment with the axis of rotation 38.
  • both exhaust gas and air can initially flow into the intake duct 12, since both flow cross-sections surrounding the valve seats 50, 52 are at least partially released.
  • the air flow is passed on largely without turbulence, since lateral wings 62 of the first flap part 44 significantly reduce the flow around the first flap part 44, which would lead to increased vortex formation.
  • a directed flow is established, which also significantly reduces sudden mixing of the cold air flow with the warm recirculated exhaust gas flow, so that condensation of the water vapor present in the exhaust gas flow is reduced.
  • first valve seat 50 In order to ensure a tight seal on the first valve seat 50 at the end of the rotary movement in the first end position, its shape is adapted to the shape of the first flap part 44, so that this flap part 44, as shown in FIG Figure 1 is shown, rests axially against the first valve seat 50 all the way round.
  • a plane 64 which is spanned by the first valve seat 50, is arranged at an angle of approximately 75 ° to a second plane 66, which is spanned by the second valve seat 52 is, so that the total angle of rotation of the shaft 36 or of the control body 42 between the two end positions is relatively small, whereby a significantly increased percentage Rotation angle range an approximately linear regulation of the air flow and the recirculated exhaust gas mass flow is achieved.
  • these planes 64, 66 are each tilted towards the shaft 36 compared to their central axes 20, 34, so that a closing force that is uniformly high over the circumference of the valve seat is also generated
  • the control device described is therefore suitable for very precise metering and directed, largely eddy-free guidance of an exhaust gas mass flow and an air mass flow to the internal combustion engine.
  • a downstream compressor can be directed against the flow, condensation of the water vapor in the exhaust gas flow and overall pressure losses due to undesired vortex formation can be reduced and thus the performance of an internal combustion engine or a downstream compressor can be improved.
  • the second housing part can be made smaller, since the cutout otherwise required for the flap in order to be able to move it into the second end position is not required.
  • valve seats and their tilt angle to the central axes can be changed or the position of the channels can be changed to one another.
  • the shape of the valve body should be adapted to the existing channel so that the surface can be round, oval or, if necessary, angular, depending on the shape of the inner wall surface.

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

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 zumindest eine Mündung des Abgasrückführkanals ausgebildet sind, einer als Drehachse dienenden Welle, die im Gehäuse bezüglich des Luftstroms stromaufwärts der Mündung des Abgasrückführkanals und außerhalb des Durchströmungsquerschnitts angeordnet ist und senkrecht zu den Mittelachsen des Ansaugkanals und des Abgasrückführkanals angeordnet ist, einem Regelkörper, der exzentrisch an der Welle befestigt ist, einem ersten Kanalabschnitt in einem ersten Gehäuseteil, an dessen stromabwärtigen Ende ein erster Ventilsitz ausgebildet ist, gegen den der Regelkörper in einer ersten Endstellung anliegt, und dessen Außenumfang kleiner ist als der Außenumfang eines sich stromabwärtig anschließenden zweiten Kanalabschnitts und einem zweiten Ventilsitz am zweiten Kanalabschnitt, an dem der Regelkörper in einer zweiten Endstellung anliegt, in der der Regelkörper den Abgasrückführkanal verschließt.The invention relates to a control device for an internal combustion engine with an intake channel, an exhaust gas recirculation channel that opens into the intake channel, a housing in which the intake channel and at least one mouth of the exhaust gas recirculation channel are formed, a shaft serving as a rotation axis, which is upstream in the housing with respect to the air flow the mouth of the exhaust gas recirculation duct and outside the flow cross-section and is arranged perpendicular to the central axes of the intake duct and the exhaust gas recirculation duct, a regulating body which is eccentrically attached to the shaft, a first duct section in a first housing part, at the downstream end of which a first valve seat is formed against which the regulating body rests in a first end position, and the outer circumference of which is smaller than the outer circumference of a downstream second duct section and a second valve seat on the second duct section on which the regulating body in a second end position, in which the control body closes the exhaust gas recirculation duct.

Regelvorrichtungen werden in Verbrennungskraftmaschinen genutzt, um Abgas- oder Luftmengen zu regeln, die abgeführt oder der Verbrennung zugeführt werden sollen. Auch Kombinationen dieser Regelventile, bei denen zwei Ventilkörper über eine gemeinsame Stellvorrichtung betätigt werden, sind bekannt. Insbesondere wurden Kombinationen eines Abgasrückführventils mit einer Drosselklappe offenbart. Bei diesen Ausführungen mündet der Abgasrückführkanal 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 eine Erhöhung des Druckgefälles im Abgasrückführkanal zur Folge hat, wodurch der Anteil des Abgases im Vergleich zur angesaugten Luftmenge erhöht wird. Eine derartige Anordnung wird beispielsweise in der DE 27 03 687 A1 offenbart.Control devices are used in internal combustion engines to regulate the amount of exhaust gas or air that is to be discharged or fed to combustion. Combinations of these control valves, in which two valve bodies are actuated via a common adjusting device, are also known. In particular, combinations of an exhaust gas recirculation valve with a throttle valve have been disclosed. In these designs, the exhaust gas recirculation channel opens into the air intake channel immediately downstream of the flap serving as a throttle valve. At If the exhaust gas recirculation rate is increased, the throttle valve is closed to the same extent when the exhaust gas recirculation valve is opened, which increases the pressure drop 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 27 03 687 A1 disclosed.

Aus der DE 10 2014 114 968 A1 ist ebenfalls eine Regelvorrichtung bekannt, bei der zwei parallel angeordnete Klappen über eine gemeinsame exzentrisch angeordnete 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 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 umlaufende Anschläge ausgebildet, gegen die die Klappen in ihrer den jeweiligen Kanal verschließenden Stellung umlaufend aufliegen. Die Drehwelle ist an einer Gehäusewand zwischen der Mündung des Abgasrückführkanals und dem Ventilsitz im Luftansaugkanal angeordnet, jedoch außerhalb des Durchströmungsquerschnitts des stromaufwärtigen Kanalabschnitts angeordnet.From the DE 10 2014 114 968 A1 A regulating device is also known in which two flaps arranged in parallel are actuated via a common eccentrically arranged rotating shaft, so that when the two flaps rotate, the first flap moves away from the valve seat of the air intake duct, while the second flap approaches the valve seat of the exhaust gas recirculation duct 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 circumferential 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 channel and the valve seat in the air intake channel, but is arranged outside the flow cross section of the upstream channel section.

Weitere Regelvorrichtungen sind aus EP 3012445 A1 , DE 102014200699 A1 , EP1707790 A1 und WO2017/097541 A1 bekannt.Further control devices are off EP 3012445 A1 , DE 102014200699 A1 , EP1707790 A1 and WO2017 / 097541 A1 known.

Durch diese bekannten Anordnungen wird zwar eine ausreichende Regelbarkeit des Abgasstromes und des Luftstromes gewährleistet, jedoch besteht ein erhöhter Druckverlust bei der Durchströmung des Ansaugkanals sowohl in der den Ansaugkanal vollständig öffnenden Position als auch in einer den Ansaugkanal drosselnden Position. Des Weiteren entstehen bei einer Anordnung der Regelvorrichtung vor einem Verdichter Probleme bezüglich einer Kondensatbildung bei Mischung des Abgasstroms mit dem Luftstrom, welche zu Schäden am Verdichter führt.These known arrangements ensure sufficient controllability of the exhaust gas flow and the air flow, but there is an increased pressure loss when flowing through the intake channel both in the position that completely opens the intake channel and in a position that restricts the intake channel. Furthermore, when the control device is arranged upstream of a compressor, problems arise with regard to the formation of condensate when the exhaust gas flow is mixed with the air flow, which leads to damage to the compressor.

Es ist daher Aufgabe der Erfindung, eine Regelvorrichtung für eine Verbrennungskraftmaschine zu schaffen, mit der die Strömungsverluste in den unterschiedlichen Stellungen des Regelkörpers möglichst gering gehalten werden, um auch die Füllung eines Verbrennungsmotors und die Anströmung eines nachfolgenden Verdichters verbessern zu können. Zusätzlich soll die Kondensatbildung im Mischgasstrom stromabwärts des Abgasrückführkanals möglichst weitgehend ausgeschlossen werden, um Schäden an einem nachfolgenden Verdichter zu verhindern.It is therefore the object of the invention to create a control device for an internal combustion engine with which the flow losses in the different positions of the control body are kept as low as possible in order to also improve the filling of an internal combustion engine and the flow to a downstream compressor. In addition, the formation of condensate in the mixed gas flow downstream of the exhaust gas recirculation duct should be excluded as far as possible in order to prevent damage to a downstream compressor.

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 die Form einer zum Inneren des Ansaugkanals weisenden Oberfläche des Regelkörpers in der zweiten Endstellung in einem Querschnitt senkrecht zur Mittelachse des ersten Gehäuseteils über einen Winkel von mindestens 90° einer an den Regelkörper angrenzenden Innenwandfläche des ersten Kanalabschnitts entspricht, wird der erste Kanalabschnitt über einen Umfangsabschnitt im Wesentlichen störungsfrei verlängert, wodurch Wirbel im Bereich des Abgaseinlasses oder an den Außenseiten des Regelkörpers verhindert werden, so dass eine deutliche Reduzierung der Druckverluste erreicht wird. Gleichzeitig wird die Mischung des warmen Abgasstroms mit dem kalten Luftstrom durch diese Strömungsführung verzögert, wodurch die Menge anfallenden Kondensats verringert wird, so dass ein nachfolgender Verdichter vor Schäden durch flüssiges Wasser geschützt wird.Because the shape of a surface of the control body facing the inside of the intake channel in the second end position corresponds in a cross section perpendicular to the central axis of the first housing part over an angle of at least 90 ° to an inner wall surface of the first channel section adjoining the control body, the first channel section becomes over a circumferential section is extended essentially without interference, as a result of which eddies in the area of the exhaust gas inlet or on the outside of the regulating body are prevented, so that a significant reduction in pressure losses is achieved. At the same time, the mixing of the warm exhaust gas flow with the cold air flow is delayed by this flow guidance, whereby the amount of condensate is reduced, so that a downstream compressor is protected from damage by liquid water.

Vorzugsweise entspricht die Form der zum Inneren des Ansaugkanals weisenden Oberfläche des Regelkörpers in der zweiten Endstellung in einem Querschnitt senkrecht zur Mittelachse über einen halben Umfang der an den Regelkörper angrenzenden Innenwandfläche des ersten Kanalabschnitts. So werden Toträume, in denen sich Wirbel bilden können, vermieden, da auf die sonst notwendige Querschnittsaufweitung für den Klappenfreilauf verzichtet werden kann. Dies bedeutet, dass der Ansaugkanal im Bereich des Regelkörpers in der den Ansaugkanal freigebenden Stellung des Regelkörpers weitestgehend störungsfrei verlängert wird, da der sich aufweitende Bereich des Gehäuses, in den der Regelkörper schwenkt, durch den Regelkörper vom durchströmten Bereich getrennt wird, der nunmehr einen geraden Verlauf aufweist. Auch in den Positionen, in denen ein Drosseln des Ansaugkanals erfolgt, wird ein weitestgehend stetiger Übergang zwischen dem ersten Kanalabschnitt und dem Kanalabschnitt, in dem der Regelkörper gedreht wird, erreicht, so dass auch hier die Wirbelbildung und damit einhergehende Druckverluste verringert werden, so das auch die Anströmung eines nachfolgenden Verdichters verbessert wird. Die Drosselwirkung wird ebenfalls verstärkt.In the second end position, the shape of the surface of the regulating body facing the inside of the intake duct corresponds in a cross section perpendicular to the central axis over half a circumference of the inner wall surface of the first duct section adjoining the regulating body. This creates dead spaces in which eddies can form avoided, since the otherwise necessary cross-sectional expansion for the flap freewheel can be dispensed with. This means that the suction channel in the area of the control body is lengthened as far as possible without interference in the position of the control body that releases the intake channel, since the expanding area of the housing into which the control body pivots is separated by the control body from the area that is flown through, which is now a straight Has course. Even in the positions in which the intake duct is throttled, a largely steady transition between the first duct section and the duct section in which the control body is rotated is achieved, so that here too the formation of eddies and the associated pressure losses are reduced the flow to a downstream compressor is also improved. The throttling effect is also increased.

In einer weiterführenden vorteilhaften Ausführungsform erstreckt sich der Regelkörper in der zweiten Endstellung bis vor einen dritten Kanalabschnitt, dessen Innenumfang kleiner ist als der Innenumfang des zweiten Kanalabschnitts, so dass auch ein stetiger Verlauf ohne Querschnittssprünge zwischen dem zweiten und dem dritten Kanalabschnitt bei den Ansaugkanal freigebendem Regelkörper hergestellt werden kann. So kann auch in diesem Bereich der Druckverlust gering gehalten werden.In a further advantageous embodiment, the regulating body extends in the second end position up to a third duct section, the inner circumference of which is smaller than the inner circumference of the second duct section, so that a continuous course without cross-sectional jumps between the second and third duct sections in the regulating body releasing the intake duct can be produced. In this way, the pressure loss can also be kept low in this area.

In einer bevorzugten Ausbildung der Erfindung ist der erste Ventilsitz durch ein axiales Ende eines ersten Gehäuseteils des Gehäuses gebildet, welches den ersten Kanalabschnitt ausbildet und in ein zweites Gehäuseteil des Gehäuses ragt, welches zumindest den zweiten Kanalabschnitt bildet. Auf diese Weise kann der Ventilsitz auf einfache Weise vor dem Zusammenbau bearbeitet werden. Zusätzlich ist eine vollflächige Auflage des Regelkörpers auf dem ersten Ventilsitz zum Verschließen des Ansaugkanals einfach herzustellen, da das erste Gehäuseteil in das zweite hineinragt und somit eine axiale Anlagefläche zur Verfügung stellt, weiche einen dichten Verschluss ermöglicht.In a preferred embodiment of the invention, the first valve seat is formed by an axial end of a first housing part of the housing which forms the first channel section and protrudes into a second housing part of the housing which forms at least the second channel section. In this way, the valve seat can be machined in a simple manner before assembly. In addition, a full-surface support of the control body on the first valve seat to close the intake channel is easy to produce, since the first housing part is in the second protrudes and thus provides an axial contact surface which enables a tight seal.

In einer hierzu weiterführenden Ausführung ist das erste Gehäuseteil über einen Flansch mit dem zweiten Gehäuseteil verbunden. Dies ermöglicht eine einfache Montage bei gleichzeitig hoher Dichtigkeit zwischen den Gehäuseteilen.In a further embodiment, the first housing part is connected to the second housing part via a flange. This enables simple assembly with a high level of tightness between the housing parts.

Vorzugsweise liegt der Regelkörper in seiner ersten Endstellung vollständig umlaufend gegen den ersten Ventilsitz am Ende des ersten Gehäuseteils an. Dies ermöglicht einen dichten Verschluss des Ansaugkanals durch die axiale Anlage. Hierdurch wirkt auch eine große Schließkraft des Regelkörpers auf den Ventilsitz, da die in Axialrichtung wirkende Komponente der durch das aufgebrachte Drehmoment resultierenden Kraft groß ist. Somit können kleinere Aktoren verwendet werden.In its first end position, the regulating body preferably lies completely circumferentially against the first valve seat at the end of the first housing part. This enables a tight closure of the intake channel through the axial contact. As a result, a large closing force of the control body also acts on the valve seat, since the component acting in the axial direction of the force resulting from the applied torque is large. This means that smaller actuators can be used.

In einer bevorzugten Ausführungsform verläuft die Mittelachse des ersten Kanalabschnitts parallel zu der Mittelachse des dritten Kanalabschnitts. So kann eine Strömungsführung ohne Absätze und Umlenkungen hergestellt werden, wodurch der Strömungswiderstand gering gehalten wird.In a preferred embodiment, the central axis of the first channel section runs parallel to the central axis of the third channel section. In this way, a flow guide can be produced without steps and deflections, whereby the flow resistance is kept low.

Des Weiteren ist es vorteilhaft, wenn eine durch den ersten Ventilsitz aufgespannte erste Ebene in einem Winkel von 75° bis 80° zu einer durch den zweiten Ventilsitz aufgespannten zweiten Ebene angeordnet ist. Hierdurch wird der Stellbereich, in welchem lediglich geringe Volumenstromänderungen der beiden Gasströme bei relativ großen vorhandenen Stellwinkeln gering gehalten, was die Regelbarkeit deutlich verbessert.Furthermore, it is advantageous if a first plane spanned by the first valve seat is arranged at an angle of 75 ° to 80 ° to a second plane spanned by the second valve seat. As a result, the adjustment range in which only small changes in volume flow of the two gas flows with relatively large adjustment angles are kept low, which significantly improves the controllability.

In einer hierzu weiterführenden Ausführungsform schließt die erste Ebene einen spitzen Winkel zu einer Ebene, welche senkrecht zur Mittelachse des Ansaugkanals angeordnet ist, ein und die zweite Ebene einen spitzen Winkel zu einer Ebene, welche senkrecht zur Mittelachse des Abgasrückführkanals angeordnet ist, ein. Entsprechend sind die Ventilsitzflächen im Vergleich zu den Kanalmittelachsen zueinander geneigt, wodurch die Verstellwege kurz sind und eine schnelle Regelung ermöglichen.In a further embodiment, the first plane forms an acute angle to a plane which is arranged perpendicular to the central axis of the intake duct, and the second plane forms an acute angle Angle to a plane which is arranged perpendicular to the central axis of the exhaust gas recirculation duct. Correspondingly, the valve seat surfaces are inclined to one another in comparison to the channel center axes, so that the adjustment paths are short and enable rapid regulation.

Vorzugsweise weist der Regelkörper ein erstes Klappenteil, an dem die Oberfläche ausgebildet ist, auf, welches in der ersten Endstellung gegen den ersten Ventilsitz anliegt und ein zweites Klappenteil auf, welches in der zweiten Endstellung gegen den zweiten Ventilsitz anliegt, wobei die beiden Klappenteile über ein Zwischenelement mit der Welle verbunden sind. Das zweite Klappenteil besteht beispielsweise aus einer in einer Bohrung des Zwischenelementes kippbeweglich aufgenommenen Halteachse und einem daran befestigten flachen Klappenkörper. Dies vereinfacht die Herstellung des Regelkörpers.The control body preferably has a first flap part, on which the surface is formed, which rests against the first valve seat in the first end position, and a second flap part which rests against the second valve seat in the second end position, the two flap parts via a Intermediate element are connected to the shaft. The second flap part consists, for example, of a holding shaft which is received in a tiltable manner in a bore of the intermediate element and a flat flap body attached to it. This simplifies the manufacture of the control body.

Es wird somit eine Regelvorrichtung geschaffen, mit der sowohl der Luftmassenstrom im Ansaugkanal als auch der Abgasmassenstrom des Abgasrückführkanals über einen großen Stellwinkelbereich schnell und genau regelbar ist, wobei vorhandene Druckverluste minimiert werden, indem Strömungshindernisse vermieden werden und Toträume, in denen sich unerwünschte Wirbel bilden könnten reduziert werden. Stattdessen wird eine weitestgehend gleichmäßige Strömung ohne Querschnittssprünge erzeugt. Durch die reduzierte Wirbelbildung wird auch die Anströmung eines nachfolgenden Verdichters verbessert und eine Schädigung des Verdichters verhindert, indem die Mengen anfallenden Kondensats durch bessere Separation des Abgasstroms vom Luftstrom verringert werden.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 duct can be regulated quickly and precisely over a large adjustment angle range, with existing pressure losses being minimized by avoiding flow obstacles and dead spaces in which undesirable eddies could form be reduced. Instead, a largely uniform flow is generated without any changes in cross-section. The reduced eddy formation also improves the flow to a downstream compressor and prevents damage to the compressor by reducing the amount of condensate that accumulates through better separation of the exhaust gas flow from the air flow.

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 Seitenansicht einer erfindungsgemäßen Regelvorrichtung mit einem Regelkörper in einer ersten Endstellung in geschnittener Darstellung.The Figure 1 shows a side view of a control device according to the invention with a control body in a first end position in a sectional view.

Die Figur 2 zeigt eine Seitenansicht der erfindungsgemäßen Regelvorrichtung aus Figur 1 mit einem Regelkörper in einer zweiten Endstellung in geschnittener Darstellung.The Figure 2 shows a side view of the control device according to the invention Figure 1 with a control body in a second end position in a sectional view.

Die Figur 3 zeigt eine Kopfansicht der erfindungsgemäßen Regelvorrichtung aus Figur 2 mit einem Regelkörper in der zweiten Endstellung in geschnittener Darstellung.The Figure 3 shows a top view of the control device according to the invention from Figure 2 with a control body in the second end position in a sectional view.

Die erfindungsgemäße Regelvorrichtung besteht aus einem Gehäuse 10, welches einen Ansaugkanal 12 begrenzt und in dem eine Mündung 14 eines Abgasrückführkanals 16 ausgebildet ist. Der Ansaugkanal 12 verläuft im Wesentlichen in gerader Richtung, während der Abgasrückführkanal 16 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 in which an opening 14 of an exhaust gas recirculation duct 16 is formed. The intake channel 12 runs essentially in a straight direction, while the exhaust gas recirculation channel 16 opens into the intake channel 12 perpendicular to the latter.

Das Gehäuse 10 besteht aus einem ersten, im Wesentlichen rohrförmig ausgebildeten Gehäuseteil 18, welches einen ersten Kanalabschnitt 19 bildet und dessen stromabwärtiges Ende schräg ausgebildet ist und einen Winkel α von etwa 75° zu einer Mittelachse 20 des Gehäuseteils 18 einschließt. Das stromabwärtige Ende des ersten Gehäuseteils 18 ist im Innern eines zweiten Gehäuseteils 22 angeordnet, beziehungsweise wird in das zweite Gehäuseteil 22 bis zur Anlage eines Flansches 24 eingeschoben, über den das erste Gehäuseteil 18 mittels Schrauben 26 am zweiten Gehäuseteil 22 befestigt ist. Das zweite Gehäuseteil 22 bildet einen zweiten Kanalabschnitt 28, in dem eine Öffnung 30 ausgebildet ist, welche in Strömungsrichtung in kurzem Abstand hinter dem schrägen Ende des ersten Gehäuseteils 18 angeordnet ist und welches als Aufnahme für ein drittes Gehäuseteil 32 dient, welches die Mündung 14 des Abgasrückführkanals 16 bildet, dessen Mittelachse 34 senkrecht zur Mittelachse 20 des Ansaugkanals 12 angeordnet ist,The housing 10 consists of a first, essentially tubular housing part 18, which forms a first channel section 19 and the downstream end of which is inclined and includes an angle α of approximately 75 ° to a central axis 20 of the housing part 18. The downstream end of the first housing part 18 is arranged in the interior of a second housing part 22, or is pushed into the second housing part 22 until a flange 24 abuts, via which the first housing part 18 is fastened to the second housing part 22 by means of screws 26. The second housing part 22 forms a second channel section 28 in which an opening 30 is formed, which is arranged in the flow direction at a short distance behind the inclined end of the first housing part 18 and which serves as a receptacle for a third housing part 32, which the mouth 14 of the Forms exhaust gas recirculation duct 16, the central axis 34 of which is arranged perpendicular to the central axis 20 of the intake duct 12,

Im Gehäuse 10 ist eine Welle 36 drehbar angeordnet, die über einen nicht sichtbaren Aktor betätigt werden kann. Die Drehachse 38 dieser Welle 36 ist senkrecht zu den Mittelachsen 20, 34 angeordnet und befindet sich zwischen der zur Welle 36 stromabwärtigen Mündung 14 des Abgasrückführkanals 16 und dem axialen Ende des ersten Gehäuseteils 18 und unmittelbar stromabwärts des ersten Gehäuseteils 18. Der Gesamtquerschnitt des ersten Gehäuseteils 18 ist kleiner als der des zweiten Gehäuseteils 22 des Ansaugkanals 12, wobei das erste Gehäuseteil 18 derart am zweiten Gehäuseteil 22 befestigt ist, dass eine im Bereich der Mündung 14 des Abgasrückführkanals 16 ausgebildete Ausnehmung 40 außerhalb des Durchströmungsquerschnitts angeordnet ist, in der die Welle 36 das zweite Gehäuseteil 22 durchdringend angeordnet ist.A shaft 36 is rotatably arranged in the housing 10 and can be actuated via an actuator which is not visible. The axis of rotation 38 of this shaft 36 is arranged perpendicular to the central axes 20, 34 and is located between the mouth 14 of the exhaust gas recirculation duct 16 downstream of the shaft 36 and the axial end of the first housing part 18 and immediately downstream of the first housing part 18. The overall cross section of the first housing part 18 is smaller than that of the second housing part 22 of the intake duct 12, the first housing part 18 being fastened to the second housing part 22 in such a way that a recess 40 formed in the region of the mouth 14 of the exhaust gas recirculation duct 16 is arranged outside the flow cross-section in which the shaft 36 the second housing part 22 is arranged penetrating.

An dieser exzentrisch im Ansaugkanal 12 angeordneten Welle 36 ist ein Regelkörper 42 befestigt, der innerhalb des zweiten Kanalabschnitts 28 drehbar angeordnet ist und aus einem ersten Klappenteil 44 sowie einem zweiten Klappenteil 45 besteht, welches eine Halteachse 46 und einen daran kippbeweglich befestigten Klappenkörper 48 aufweist, wobei die Halteachse 46 in einer Bohrung eines Zwischenelementes 49 kippbeweglich befestigt ist. Das Zwischenelement 49 ist entweder mit dem ersten Klappenteil 44 einstückig hergestellt oder mit diesem verbunden und weist eine Verbindung zur Welle 36 auf. Bei Drehung der Welle 36 wird somit der erste Klappenteil 44 in einer ersten Endstellung gegen das Ende des ersten Gehäuseteils 18 gedreht, welches entsprechend als erster Ventilsitz 50 dient, während bei Drehung in entgegengesetzter Richtung der Klappenkörper 48 in einer zweiten Endstellung gegen ein Ende der Mündung 14 des Abgasrückführkanals 16 gedreht wird, welches als zweiter Ventilsitz 52 dient. Entsprechend wird bei Drehung der Welle 36 in dem Maße in dem der erste Klappenteil 44 den Ansaugkanal 12 freigibt, der Abgasrückführkanal 16 durch den Klappenkörper 48 geschlossen und umgekehrt. Die kippbewegliche Befestigung des zweiten Klappenteils 45 führt bei dieser Drehbewegung der Welle 36 in eine zweite Endstellung, in der der Klappenkörper 48 auf dem zweiten Ventilsitz 52 aufliegt, dazu, dass ein vollständiger dichter Verschluss des Abgasrückführkanals 16 erfolgt, da der Klappenkörper 48 seine Stellung durch die mögliche Kippbewegung an die Lage des zweiten Ventilsitzes 52 anpassen kann, auch wenn dieser nicht vollständig in der Flucht zur Drehachse 38 liegt.A regulating body 42 is attached to this eccentrically arranged shaft 36 in the intake channel 12, which is arranged rotatably within the second channel section 28 and consists of a first flap part 44 and a second flap part 45, which has a holding axis 46 and a flap body 48 attached to it such that it can tilt, wherein the holding shaft 46 is mounted in a bore of an intermediate element 49 such that it can tilt. The intermediate element 49 is either produced in one piece with the first flap part 44 or connected to it and has a connection to the shaft 36. When the shaft 36 is rotated, the first flap part 44 is rotated in a first end position against the end of the first housing part 18, which accordingly serves as the first valve seat 50, while when rotated in the opposite direction, the flap body 48 is in a second end position against one end of the mouth 14 of the exhaust gas recirculation duct 16, which serves as a second valve seat 52, is rotated. Correspondingly, upon rotation of the shaft 36, to the extent that the first flap part 44 releases the intake duct 12, the Exhaust gas recirculation duct 16 is closed by the flap body 48 and vice versa. The tiltable fastening of the second flap part 45 leads to this rotational movement of the shaft 36 in a second end position, in which the flap body 48 rests on the second valve seat 52, that a completely tight closure of the exhaust gas recirculation channel 16 takes place, since the flap body 48 is in its position can adapt the possible tilting movement to the position of the second valve seat 52, even if it is not completely in alignment with the axis of rotation 38.

In der in Figur 2 dargestellten zweiten Endstellung des Regelkörpers 42 liegt der Klappenkörper 48 auf dem Ventilsitz 52 des Abgasrückführkanals 16 auf, während der erste Klappenteil 44 den Ansaugkanal 12 vollständig freigibt. In dieser Position wird der erste Kanalabschnitt 19 etwa über seinen halben näher zum Abgasrückführkanal 16 weisenden Umfang durch eine entsprechend geformte Oberfläche 54 des Regelkörpers 42 verlängert, was besonders in der Figur 3 gut zu erkennen ist. Dies bedeutet, dass in einem Querschnitt zur Mittelachse 20 des ersten Gehäuseteils 18 im Bereich des Regelkörpers 42 die Form der zur Mittelachse 20 weisenden Oberfläche 54 des Regelkörpers 42 über einen definierten Umfangsabschnitt der Form einer Innenwandfläche 56 des ersten Gehäuseteils 18, welche an den Regelkörper 42 grenzt, entspricht. Dies hat zur Folge, dass der einströmende Luftstrom weitestgehend ohne Strömungshindernisse vom ersten Kanalabschnitt 19 in den zweiten Kanalabschnitt 28 strömen kann. Da der Regelkörper 42 sich in diesem Zustand auch weitestgehend durch den zweiten Kanalabschnitt 28 hindurch bis zu einem dritten Kanalabschnitt 58 erstreckt, dessen Mittelachse 60 parallel zur Mittelachse 20 des ersten Gehäuseteils 18 verläuft und lediglich geringfügig dazu versetzt angeordnet ist und dessen Umfang im Vergleich zum zweiten Kanalabschnitt 28 wieder reduziert ist, erfolgt auch hier eine weitestgehend ungestörte Strömung entlang des Ansaugkanals 12, so dass auftretende Druckverluste minimiert werden.In the in Figure 2 The second end position of the regulating body 42 shown, the flap body 48 rests on the valve seat 52 of the exhaust gas recirculation duct 16, while the first flap part 44 completely releases the intake duct 12. In this position, the first channel section 19 is lengthened approximately over half of the circumference pointing closer to the exhaust gas recirculation channel 16 by a correspondingly shaped surface 54 of the control body 42, which is particularly the case in FIG Figure 3 is easy to see. This means that in a cross-section to the central axis 20 of the first housing part 18 in the area of the control body 42 the shape of the surface 54 of the control body 42 facing the central axis 20 over a defined circumferential section of the shape of an inner wall surface 56 of the first housing part 18, which is attached to the control body 42 borders, corresponds. As a result, the inflowing air flow can flow from the first duct section 19 into the second duct section 28 largely without any flow obstacles. Since the regulating body 42 in this state extends as far as possible through the second channel section 28 to a third channel section 58, the central axis 60 of which runs parallel to the central axis 20 of the first housing part 18 and is only arranged slightly offset and its circumference compared to the second Channel section 28 is reduced again, here too a largely undisturbed flow occurs along the intake channel 12, so that pressure losses that occur are minimized.

Wird der Regelkörper 42 aus dieser zweiten Endstellung in seine in der Figur 1 dargestellten, ersten Endstellung gedreht, so können zunächst sowohl Abgas als auch Luft in den Ansaugkanal 12 strömen, da beide von den Ventilsitzen 50, 52 umgebende Durchströmungsquerschnitte zumindest teilweise freigegebenen sind. Im Gegensatz zu bekannten Ausführungen wird jedoch der Luftstrom weitestgehend turbulenzfrei weitergeleitet, da seitliche Flügel 62 des ersten Klappenteils 44 ein Umströmen des ersten Klappenteils 44, was zu erhöhter Wirbelbildung führen würde, deutlich reduziert. Stattdessen wird eine gerichtete Strömung hergestellt, durch die auch eine plötzliche Vermischung des kalten Luftstroms mit dem warmen zurückgeführten Abgasstrom deutlich verringert wird, so dass ein Kondensieren des im Abgasstrom vorhandenen Wasserdampfes reduziert wird. Hierdurch wird einerseits die Belastung eines nachfolgenden Verdichters durch kondensiertes Wasser deutlich gesenkt und andererseits die Anströmung des Verdichters deutlich verbessert, da eine gerichtete Strömung gezielt zum Verdichterrad geführt werden kann, was wiederum zu einem erhöhten Wirkungsgrad des Verdichters führt.If the control body 42 from this second end position in its in the Figure 1 If the first end position shown is rotated, both exhaust gas and air can initially flow into the intake duct 12, since both flow cross-sections surrounding the valve seats 50, 52 are at least partially released. In contrast to known designs, however, the air flow is passed on largely without turbulence, since lateral wings 62 of the first flap part 44 significantly reduce the flow around the first flap part 44, which would lead to increased vortex formation. Instead, a directed flow is established, which also significantly reduces sudden mixing of the cold air flow with the warm recirculated exhaust gas flow, so that condensation of the water vapor present in the exhaust gas flow is reduced. On the one hand, this significantly reduces the load on a downstream compressor from condensed water and, on the other hand, significantly improves the flow to the compressor, since a directed flow can be directed to the compressor wheel, which in turn increases the efficiency of the compressor.

Um am Ende der Drehbewegung in der ersten Endstellung einen dichten Verschluss am ersten Ventilsitz 50 zu gewährleisten, ist dieser bezüglich seiner Form an die Form des ersten Klappenteils 44 angepasst, so dass dieses Klappenteil 44, wie es in Figur 1 dargestellt ist, vollständig umlaufend axial gegen den ersten Ventilsitz 50 anliegt.In order to ensure a tight seal on the first valve seat 50 at the end of the rotary movement in the first end position, its shape is adapted to the shape of the first flap part 44, so that this flap part 44, as shown in FIG Figure 1 is shown, rests axially against the first valve seat 50 all the way round.

Um auch in den Zwischenstellungen eine möglichst gute und schnelle Regelung erreichen zu können, ist eine Ebene 64, die durch den ersten Ventilsitz 50 aufgespannt wird, in einem Winkel von etwa 75° zu einer zweiten Ebene 66 angeordnet, die durch den zweiten Ventilsitz 52 aufgespannt wird, so dass der Gesamtdrehwinkel der Welle 36 beziehungsweise des Regelkörpers 42 zwischen den beiden Endstellungen relativ gering ist, wodurch über einen deutlich erhöhten prozentualen Drehwinkelbereich eine etwa lineare Regelung des Luftstroms und des zurückgeführten Abgasmassenstroms erreicht wird.In order to be able to achieve the best and fastest possible control in the intermediate positions, a plane 64, which is spanned by the first valve seat 50, is arranged at an angle of approximately 75 ° to a second plane 66, which is spanned by the second valve seat 52 is, so that the total angle of rotation of the shaft 36 or of the control body 42 between the two end positions is relatively small, whereby a significantly increased percentage Rotation angle range an approximately linear regulation of the air flow and the recirculated exhaust gas mass flow is achieved.

Zusätzlich sind diese Ebenen 64, 66 jeweils zur Welle 36 im Vergleich zu ihren Mittelachsen 20, 34 gekippt, so dass auch eine über den Umfang des Ventilsitzes gleichmäßig hohe Schließkraft erzeugt wird,In addition, these planes 64, 66 are each tilted towards the shaft 36 compared to their central axes 20, 34, so that a closing force that is uniformly high over the circumference of the valve seat is also generated

Die beschriebene Regelvorrichtung eignet sich somit zur sehr exakten Dosierung und gerichteten, weitestgehend wirbelfreien Führung eines Abgasmassenstroms und eines Luftmassenstroms zum Verbrennungsmotor. Dabei kann ein nachfolgender Verdichter gerichtet angeströmt werden, Kondensation des Wasserdampfes im Abgasstrom sowie insgesamt auftretende Druckverluste durch unerwünschte Wirbelbildung reduziert werden und somit die Leistung eines Verbrennungsmotors beziehungsweise eines nachfolgenden Verdichters verbessert werden. Zusätzlich kann das zweite Gehäuseteil verkleinert werden, da der sonst für die Klappe notwendige Freischnitt, um diese in die zweite Endstellung fahren zu können, nicht erforderlich ist.The control device described is therefore suitable for very precise metering and directed, largely eddy-free guidance of an exhaust gas mass flow and an air mass flow to the internal combustion engine. A downstream compressor can be directed against the flow, condensation of the water vapor in the exhaust gas flow and overall pressure losses due to undesired vortex formation can be reduced and thus the performance of an internal combustion engine or a downstream compressor can be improved. In addition, the second housing part can be made smaller, since the cutout otherwise required for the flap in order to be able to move it into the second end position is not required.

Es sollte deutlich sein, dass der Schutzbereich der vorliegenden Anmeldung nicht auf das beschriebene Ausführungsbeispiel beschränkt ist. Insbesondere kann die Lage der Ventilsitze und deren Kippwinkel zu den Mittelachsen verändert werden oder die Lage der Kanäle zueinander geändert werden. Die Form des Klappenkörpers sollte jeweils an den vorhandenen Kanal angepasst werden so dass die Oberfläche je nach Form der Innenwandfläche rund, oval oder gegebenenfalls eckig sein kann.It should be clear that the scope of protection of the present application is not limited to the exemplary embodiment described. In particular, the position of the valve seats and their tilt angle to the central axes can be changed or the position of the channels can be changed to one another. The shape of the valve body should be adapted to the existing channel so that the surface can be round, oval or, if necessary, angular, depending on the shape of the inner wall surface.

Claims (10)

  1. Control device for an internal combustion engine comprising
    an intake channel (12),
    an exhaust gas recirculation channel (16) opening into the intake channel (12),
    a housing (10) in which the intake channel (12) and at least one mouth (14) of the exhaust gas recirculation channel (16) are formed,
    a shaft (36) serving as a rotary axis (38), which is disposed in the housing (10) upstream of the mouth (14) of the exhaust gas recirculation channel (16) and is arranged outside the flow cross section of a first channel section (19) of the intake channel (12),
    a control body (42) attached eccentrically to the shaft (36),
    a first channel section (19) in a first housing part (18), at the downstream end of which a first valve seat (50) is formed, against which the control body (42) abuts in a first end position, and the outer circumference of which is smaller than the outer circumference of a second channel section (28) adjoining in the downstream direction and
    a second valve seat (72) on the second channel section, against which the control body (42) abuts in a second end position, in which the control body (42) closes the exhaust gas recirculation channel (16),
    characterized in that
    the shape of a surface (54) of the control body (42) facing the interior of the intake channel (12) in the second end position corresponds, in a cross section perpendicular to the central axis (20) of the first housing part (18), to an inner wall surface adjacent to the control body (42) of the first channel section (19) over an angle of at least 90°.
  2. Control device for an internal combustion engine according to claim 1, characterized in that the shape of the surface (54) of the control body (42) facing the interior of the intake channel (12) in the second end position corresponds, in a cross section perpendicular to the central axis (20), to the inner wall surface (56) of the control flap (42) to the first channel section (19) over half a circumference.
  3. Control device for an internal combustion engine according to one of claims 1 or 2, characterized in that in the second end position, the control body (42) extends up to a third channel section (58), the inner circumference of which is smaller than the inner circumference of the second channel section (28).
  4. Control device for an internal combustion engine according to one of the preceding claims, characterized in that the first valve seat (50) is formed by an axial end of a first housing part (18) of the housing (10), which forms the first channel section (19) and protrudes into a second housing part (22) of the housing (10), which at least forms the second channel section (28).
  5. Control device for an internal combustion engine according to claim 4, characterized in that the first housing part (18) is connected to the second housing part (22) by a flange (24).
  6. Control device for an internal combustion engine according to one of the preceding claims, characterized in that in its first end position, the control body (42) rests completely circumferentially on the first valve seat (50) at the end of the first housing part (18).
  7. Control device for an internal combustion engine according to one of claims 3 to 6, characterized in that the central axis (20) of the first channel section (19) extends parallel to the central axis (60) of the third channel section (58).
  8. Control device for an internal combustion engine according to one of the preceding claims, characterized in that a first plane (64) spanned by the first valve seat (50) is arranged under an angle of 75° to 80° to a second plane (66) spanned by the second valve seat (52).
  9. Control device for an internal combustion engine according to claim 8, characterized in that the first plane (64) forms an acute angle with respect to a plane arranged perpendicular to the central axis (20) of the intake channel (12), and the second plane (66) forms an acute angle with respect to a plane arranged perpendicular to the central axis (34) of the exhaust gas recirculation channel (16).
  10. Control device for an internal combustion engine according to one of the preceding claims, characterized in that the control body (42) comprises a first flap part (44) on which the surface (54) is formed, which flap part abuts against the first valve seat (50) in the first end position, and a second flap part (45) which abuts against the second valve seat (52) in the second end position, the two flap parts (44, 45) being connected to the shaft (36) via an intermediate element (49).
EP17793661.4A 2016-11-14 2017-11-03 Control device for an internal combustion engine Active EP3538753B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016121705.0A DE102016121705B4 (en) 2016-11-14 2016-11-14 Regulating device for an internal combustion engine
PCT/EP2017/078171 WO2018087004A1 (en) 2016-11-14 2017-11-03 Control device for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP3538753A1 EP3538753A1 (en) 2019-09-18
EP3538753B1 true EP3538753B1 (en) 2020-09-30

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EP (1) EP3538753B1 (en)
DE (1) DE102016121705B4 (en)
WO (1) WO2018087004A1 (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017097541A1 (en) * 2015-12-11 2017-06-15 Pierburg Gmbh Regulating device for an internal combustion engine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2703687A1 (en) 1977-01-29 1978-08-03 Bosch Gmbh Robert DEVICE FOR CONTROLLING ADDITIONAL GAS SUPPLY QUANTITIES INTO THE SUCTION MANIFOLD OF A COMBUSTION MACHINE
ES2358675T3 (en) * 2005-03-31 2011-05-12 Cooper-Standard Automotive (Deutschland) Gmbh EXHAUST GAS RECIRCULATION SYSTEM.
DE102014200699A1 (en) * 2014-01-16 2015-07-16 Ford Global Technologies, Llc Low-pressure EGR valve
DE102014114968B4 (en) 2014-10-15 2021-01-21 Pierburg Gmbh Control device for an internal combustion engine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017097541A1 (en) * 2015-12-11 2017-06-15 Pierburg Gmbh Regulating device for an internal combustion engine

Also Published As

Publication number Publication date
DE102016121705A1 (en) 2018-05-17
WO2018087004A1 (en) 2018-05-17
DE102016121705B4 (en) 2018-06-14
EP3538753A1 (en) 2019-09-18

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