EP2079908A1 - Turbocharger - Google Patents

Turbocharger

Info

Publication number
EP2079908A1
EP2079908A1 EP07819253A EP07819253A EP2079908A1 EP 2079908 A1 EP2079908 A1 EP 2079908A1 EP 07819253 A EP07819253 A EP 07819253A EP 07819253 A EP07819253 A EP 07819253A EP 2079908 A1 EP2079908 A1 EP 2079908A1
Authority
EP
European Patent Office
Prior art keywords
turbocharger
valve
compressor
angle
reference surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07819253A
Other languages
German (de)
French (fr)
Inventor
Klaus-Peter DÖRLE
Oliver Schumnig
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.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BorgWarner Inc filed Critical BorgWarner Inc
Publication of EP2079908A1 publication Critical patent/EP2079908A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/16—Control of the pumps by bypassing charging air
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22C—FOUNDRY MOULDING
    • B22C9/00—Moulds or cores; Moulding processes
    • B22C9/10—Cores; Manufacture or installation of cores
    • B22C9/101—Permanent cores
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/105—Final actuators by passing part of the fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/21—Manufacture essentially without removing material by casting
    • F05D2230/211—Manufacture essentially without removing material by casting by precision casting, e.g. microfusing or investment casting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/30—Arrangement of components
    • F05D2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
    • F05D2250/314—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being inclined in relation to each other
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a turbocharger according to the preamble of claim 1.
  • the throttle valve mounted behind the compressor of the turbocharger in the air collector.
  • the throttle closes and the compressor of the turbocharger would promote due to its inertia air against a nearly closed volume. This would mean that the compressor would no longer be able to pump continuously and backflows would form. The compressor would pump. The speed of the turbocharger would therefore decrease very quickly.
  • turbochargers can be provided with a recirculation valve (also called a recirculation valve), which opens pressure-controlled from a certain negative pressure via a spring-loaded valve element, a connecting channel, which returns the air to the compressor inlet.
  • a recirculation valve also called a recirculation valve
  • the compressor housing which has a valve flange for the recirculation valve, mainly produced by chill casting or sand casting. Furthermore, it is also known to produce such a valve housing in die casting, but here several moldings must be joined together, since the geometry of the individual moldings is to be chosen so that they can be demoulded in the die casting. However, this increases the design effort and thus the manufacturing cost.
  • Verbhdungskanal the compressor housing which leads from the compressor spiral to the compressor inlet and the flange of the valve flange for the recirculation valve at an angle of large 0 ° to the reference side of the compressor housing, it is possible to use in die casting so-called slide, the can be pulled out of the compressor housing due to the setting of said angle to values of more than 0 ° after the casting process, which makes it possible to the compressor housing of the turbocharger according to the invention cost-effective way to produce in one piece in the die-casting.
  • a compressor housing according to the invention is defined as a self-negotiable object.
  • Fig. 1 is a perspective view of a turbocharger according to the invention for explaining the basic structure thereof;
  • FIG. 2 is a sectional view of the compressor housing according to the invention for a turbocharger according to FIG. 1.
  • turbocharger 1 serves to illustrate the principal components of a turbocharger 1 according to the invention, which, as usual, has a turbine 2 and a compressor 3, which is connected to the turbine 2 via a bearing housing 4.
  • a turbine 2 and a compressor 3 which is connected to the turbine 2 via a bearing housing 4.
  • all other conventional components such as a rotor shaft, the compressor and the turbine wheel are provided, which will not be explained in more detail below, since they are not required for the explanation of the principles of the present invention.
  • FIG. 2 the compressor housing 5 of the compressor 3 is shown in a sectional view.
  • the compressor housing 5 has a reference surface BF, which is arranged perpendicular to the turbocharger axis A L and the coil axially limited to the bearing housing side.
  • the compressor housing 5 has a valve flange 6, on which the recirculation valve explained in the introduction, which in FIG. 2 is not shown in detail, can be fastened.
  • the valve flange 6 has a flange surface 8, in which an inlet opening 10 is arranged, to which a connecting channel 9 connects to the compressor inlet 7.
  • the valve flange 6 has a valve seat 11 for the closing element, not shown, of the recirculation valve.
  • the channel axis A K is arranged at an angle ⁇ to the valve seat.
  • the flange 8 is arranged at an angle ⁇ to the reference surface BF, which, as the angle ß in the illustrated embodiment is greater than 0 ° and preferably formed as an acute angle.
  • the line BF 1 represents a parallel displacement of the reference surface BF in order to be able to represent the position of the angle ⁇ in a simplified manner.
  • valve housing 5 By choosing the angle ⁇ and ß with angular dimensions of more than 0 °, it is possible to produce the valve housing 5 in one piece by die casting, as it is possible by an appropriate choice of the angle ⁇ and ß greater than 0 °, in the range of to be cast compressor housing in which the connecting channel 9 is to arise to arrange a slide, which can be removed from the molded valve housing 5 after the casting process.
  • A inner diameter of the valve opening 10
  • a L ; G distance of the center of the valve opening 10 to the
  • Turbocharger axis A L I distance between the reference side or the reference surface BF and the center of the valve opening 10; V: distance of the intersection of the valve flange axis A VF with the spiral cross-section center to the reference surface BF; R: distance of the inner wall of the inlet nozzle 7 of the

Landscapes

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

Abstract

The invention relates to a turbocharger (1) having a turbine (2); and having a compressor (3) connected to the turbine (2) by means of a bearing housing (4), the compressor comprising a compressor housing (5), which has a reference surface (BF) perpendicular to a turbocharger axis (AL), and a valve flange (6) equipped with a valve seat (11) for a wastegate valve and a connecting channel (9) to a compressor inlet (7), wherein the valve flange (6) has a flange surface (8) that is disposed at a calculable angle (α) to the reference surface (BF) in a tilted manner, and wherein the connecting channel (9) has a channel axis (Aϰ), which is disposed at a calculable angle (ß) in a tilted manner.

Description

Turbolader turbocharger
Beschreibungdescription
Die Erfindung betrifft einen Turbolader gemäß dem Oberbegriff des Anspruches 1.The invention relates to a turbocharger according to the preamble of claim 1.
Bei aufgeladenen Ottomotoren, bei denen der gattungsgemäße Turbolader zum Einsatz kommen kann, ist die Drosselklappe, mit der die Motorlast vorgegeben wird, hinter dem Verdichter des Turboladers im Luftsammler angebracht. Bei der Gaswegnahme schließt sich die Drosselklappe und der Verdichter des Turboladers würde infolge seiner Massenträgheit Luft gegen ein nahezu geschlossenes Volumen fördern. Dies hätte zur Folge, dass der Verdichter nicht mehr kontinuierlich fördern könnte und sich Rückströmungen bilden würden. Der Verdichter würde pumpen. Die Drehzahl des Turboladers würde daher sehr schnell abnehmen .In supercharged gasoline engines, in which the generic turbocharger can be used, the throttle valve, with which the engine load is specified, mounted behind the compressor of the turbocharger in the air collector. When the gas is removed, the throttle closes and the compressor of the turbocharger would promote due to its inertia air against a nearly closed volume. This would mean that the compressor would no longer be able to pump continuously and backflows would form. The compressor would pump. The speed of the turbocharger would therefore decrease very quickly.
Um dies zu verhindern, können Turbolader mit einem Umluftventil (auch Schubumluftventil genannt) versehen werden, das druckgesteuert ab einem bestimmten Unterdruck über ein federbelastetes Ventilelement einen Verbindungskanal öffnet, der die Luft zum Verdichtereintritt zurückführt. Somit ist es möglich, dass die Drehzahl des Tυrboladers auf einem hohen Niveau bleibt und bei einem anschließenden Beschleunigungsvorgang sofort wieder Ladedruck zur Verfugung steht.In order to prevent this, turbochargers can be provided with a recirculation valve (also called a recirculation valve), which opens pressure-controlled from a certain negative pressure via a spring-loaded valve element, a connecting channel, which returns the air to the compressor inlet. Thus it is possible that the speed of Tυrboladers remains at a high level and in a subsequent acceleration process immediately boost pressure is available.
Bei bekannten Turboladern mit einem derartigen Umluftventil wird das Verdichtergehause, das einen Ventilflansch für das Umluftventil aufweist, vor allem durch Kokillenguss oder Sandguss hergestellt. Ferner ist es auch bekannt, derartige Ventilgehause im Druckguss herzustellen, wobei hier jedoch mehrere Formteile zusammengefugt werden müssen, da die Geometrie der einzelnen Formteile so zu wählen ist, dass sie im Druckguss entformbar sind. Dies erhöht jedoch den Konstruktionsaufwand und damit die Herstellungskosten.In known turbochargers with such a recirculation valve, the compressor housing, which has a valve flange for the recirculation valve, mainly produced by chill casting or sand casting. Furthermore, it is also known to produce such a valve housing in die casting, but here several moldings must be joined together, since the geometry of the individual moldings is to be chosen so that they can be demoulded in the die casting. However, this increases the design effort and thus the manufacturing cost.
Es ist daher Aufgabe der vorliegenden Erfindung, einen Turbolader der im Oberbegriff des Anspruches 1 angegebenen Art zu schaffen, dessen Verdichtergehause auf kostengünstige Art und Weise mittels Druckguss in einem Stuck herstellbar ist.It is therefore an object of the present invention to provide a turbocharger specified in the preamble of claim 1 way, the compressor housing can be produced in a cost-effective manner by means of die casting in one piece.
Die Losung dieser Aufgabe erfolgt durch die Merkmale des Anspruchs 1.The solution of this object is achieved by the features of claim 1.
Die Unteranspruche 2 bis 6 haben vorteilhafte Weiterbildungen der Erfindung zum Inhalt.The dependent claims 2 to 6 have advantageous developments of the invention to the content.
Dadurch, dass der Verbmdungskanal des Verdichtergehauses, der von der Verdichterspirale zum Verdichtereintritt fuhrt und die Flanschflache des Ventilflansches für das Umluftventil in einem Winkel von großer 0° zur Bezugsseite des Verdichtergehauses angeordnet werden, ist es möglich, bei der Druckgussherstellung sogenannte Schieber zu verwenden, die nach dem Gießvorgang aufgrund der Einstellung der genannten Winkel auf Werte von mehr als 0° aus dem Verdichtergehause herausgezogen werden können, was es möglich macht, das Verdichtergehause des erfindungsgemaßen Turboladers auf kostengünstige Art und Weise im Druckguss in einem Stück herzustellen.Characterized in that the Verbhdungskanal the compressor housing, which leads from the compressor spiral to the compressor inlet and the flange of the valve flange for the recirculation valve at an angle of large 0 ° to the reference side of the compressor housing, it is possible to use in die casting so-called slide, the can be pulled out of the compressor housing due to the setting of said angle to values of more than 0 ° after the casting process, which makes it possible to the compressor housing of the turbocharger according to the invention cost-effective way to produce in one piece in the die-casting.
In Anspruch 7 ist ein erfindungsgemäßes Verdichtergehause als selbstständig handelbares Objekt definiert.In claim 7, a compressor housing according to the invention is defined as a self-negotiable object.
Weitere Einzelheiten, Vorteile und Merkmale der vorliegenden Erfindung ergeben sich aus nachfolgender Beschreibung eines Ausführungsbeispiels anhand der Zeichnung. Es zeigt:Further details, advantages and features of the present invention will become apparent from the following description of an embodiment with reference to the drawing. It shows:
Fig. 1 eine perspektivische Darstellung eines erfindungsgemäßen Turboladers zur Erläuterung dessen prinzipiellen Aufbaus; undFig. 1 is a perspective view of a turbocharger according to the invention for explaining the basic structure thereof; and
Fig. 2 eine Schnittdarstellung des erfindungsgemäßen Verdichtergehäuses für einen Turbolader gemäß Fig. 1.2 is a sectional view of the compressor housing according to the invention for a turbocharger according to FIG. 1.
Fig. 1 dient dazu, die prinzipiellen Bauteile eines erfindungsgemäßen Turboladers 1 darzustellen, der wie üblich eine Turbine 2 und einen Verdichter 3 aufweist, der über ein Lagergehäuse 4 mit der Turbine 2 verbunden ist. Natürlich sind auch alle anderen üblichen Bauteile wie eine Läuferwelle, das Verdichterrad und das Turbinenrad vorgesehen, die jedoch nachfolgend nicht näher erläutert werden, da sie für die Erklärung der Prinzipien vorliegender Erfindung nicht erforderlich sind.1 serves to illustrate the principal components of a turbocharger 1 according to the invention, which, as usual, has a turbine 2 and a compressor 3, which is connected to the turbine 2 via a bearing housing 4. Of course, all other conventional components such as a rotor shaft, the compressor and the turbine wheel are provided, which will not be explained in more detail below, since they are not required for the explanation of the principles of the present invention.
In Fig. 2 ist in einer Schnittdarstellung das Verdichtergehäuse 5 des Verdichters 3 dargestellt.In Fig. 2, the compressor housing 5 of the compressor 3 is shown in a sectional view.
Das Verdichtergehäuse 5 weist eine Bezugsflache BF auf, die senkrecht zur Turboladerachse AL angeordnet ist und die Spirale zur Lagergehäuseseite hin axial begrenzt.The compressor housing 5 has a reference surface BF, which is arranged perpendicular to the turbocharger axis A L and the coil axially limited to the bearing housing side.
Ferner weist das Verdichtergehäuse 5 einen Ventilflansch 6 auf, an dem das eingangs erläuterte Umluftventil, das in Fig. 2 nicht näher dargestellt ist, befestigbar ist. Der Ventilflansch 6 weist hierfür eine Flanschfläche 8 auf, in der eine Eintrittsöffnung 10 angeordnet ist, an die sich ein Verbindungskanal 9 zum Verdichtereintritt 7 anschließt. Ferner weist der Ventilflansch 6 einen Ventilsitz 11 für das nicht gezeigte Schließelement des Umluftventils auf.Furthermore, the compressor housing 5 has a valve flange 6, on which the recirculation valve explained in the introduction, which in FIG. 2 is not shown in detail, can be fastened. For this purpose, the valve flange 6 has a flange surface 8, in which an inlet opening 10 is arranged, to which a connecting channel 9 connects to the compressor inlet 7. Furthermore, the valve flange 6 has a valve seat 11 for the closing element, not shown, of the recirculation valve.
Wie Fig. 2 verdeutlicht, ist die Kanalachse Aκ in einem Winkel ß zum Ventilsitz angeordnet.As FIG. 2 illustrates, the channel axis A K is arranged at an angle β to the valve seat.
Ferner ist die Flanschfläche 8 in einem Winkel α zur Bezugsfläche BF angeordnet, der, wie der Winkel ß bei der dargestellten Ausführungsform größer 0° und vorzugsweise als spitzer Winkel ausgebildet ist. Die Linie BF1 stellt eine Parallelverschiebung der Bezugsfläche BF dar, um die Lage des Winkels α vereinfacht darstellen zu können.Further, the flange 8 is arranged at an angle α to the reference surface BF, which, as the angle ß in the illustrated embodiment is greater than 0 ° and preferably formed as an acute angle. The line BF 1 represents a parallel displacement of the reference surface BF in order to be able to represent the position of the angle α in a simplified manner.
Durch die Wahl der Winkel α und ß mit Winkelmaßen von mehr als 0° ist es möglich, das Ventilgehäuse 5 in einem Stück im Druckguss herzustellen, da es durch eine entsprechende Wahl der Winkel α und ß größer 0° möglich ist, in den Bereich des zu vergießenden Verdichtergehäuses, in dem der Verbindungskanal 9 entstehen soll, einen Schieber anzuordnen, der nach dem Gießvorgang aus dem vergossenen Ventilgehäuse 5 entnommen werden kann.By choosing the angle α and ß with angular dimensions of more than 0 °, it is possible to produce the valve housing 5 in one piece by die casting, as it is possible by an appropriate choice of the angle α and ß greater than 0 °, in the range of to be cast compressor housing in which the connecting channel 9 is to arise to arrange a slide, which can be removed from the molded valve housing 5 after the casting process.
Es hat sich als besonders vorteilhaft erwiesen, wenn ß im Bereich 15-60° und α im Bereich von 0-60° liegen.It has proved to be particularly advantageous if β in the range 15-60 ° and α in the range of 0-60 °.
Obwohl die Erfindung voranstehend anhand der besonders bevorzugten Ausführungsform gemäß der Fig. 2 erläutert wurde, ist es möglich, die Winkel α und ß in verallgemeinerter Form unter Bezugnahme auf die in Fig. 2 eingezeichneten Größen zu berechnen. Diese sind wie folgt definiert: α: Neigung des Ventilflansches bzw. Stutzens 6; ß: Neigung des Verbindungskanals bzw. Querkanals 9;Although the invention has been explained above with reference to the particularly preferred embodiment according to FIG. 2, it is possible to calculate the angles α and β in a generalized form with reference to the variables shown in FIG. These are defined as follows: α: inclination of the valve flange or socket 6; ß: inclination of the connecting channel or transverse channel 9;
A: Innendurchmesser der Ventilöffnung 10;A: inner diameter of the valve opening 10;
B: Innendurchmesser eines Umluftventil-Regelkanals 12;B: inner diameter of a recirculation valve control channel 12;
C: Abstand Ventilsitz 11 zur Flanschfläche 8;C: distance valve seat 11 to the flange 8;
D: Innendurchmesser des Verbindungskanals 9;D: inner diameter of the connection channel 9;
E: Abstand von Bezugsfläche BF zu dem Schnittpunkt der AchsenE: distance from reference surface BF to the intersection of the axes
Aκ und AL, welcher durch die Ebene derA κ and A L passing through the plane of
Schaufeleintrittskanten des (nicht dargestellten)Blade leading edges of the (not shown)
Verdichterrades vorgegeben ist; F: Abstand der Spiralquerschnittsmitte zu der TurboladerachseVerdichterrades is specified; F: Distance of the spiral cross section center to the turbocharger axis
AL; G: Abstand des Mittelpunktes der Ventilöffnung 10 zu derA L ; G: distance of the center of the valve opening 10 to the
Turboladerachse AL I: Abstand zwischen der Bezugsseite bzw. der Bezugsfläche BF und dem Mittelpunkt der Ventilöffnung 10; V: Abstand des Schnittpunkts der Ventilflanschachse AVF mit der Spiralquerschnittsmitte zu der Bezugsfläche BF; R: Abstand der Innenwand des Eintrittsstutzens 7 von derTurbocharger axis A L I: distance between the reference side or the reference surface BF and the center of the valve opening 10; V: distance of the intersection of the valve flange axis A VF with the spiral cross-section center to the reference surface BF; R: distance of the inner wall of the inlet nozzle 7 of the
Turboladerachse AL Turbocharger axle A L
Unter Zugrundelegung dieser Größen berechnen sich die Winkel α und ß wie folgt:On the basis of these quantities, the angles α and β are calculated as follows:
α = arctan ( (G-F) /(1-V) )α = arctane ((G-F) / (1-V))
I- (—sinor) -E ß = arctan [ 1 ]I- (-sinor) -Eβ = arctane [1]
G + (— •cosα) - R BezugszeichenlisteG + (- • cosα) - R LIST OF REFERENCE NUMBERS
1 Turbolader1 turbocharger
2 Turbine2 turbine
3 Verdichter3 compressors
A LagergehäuseA bearing housing
5 Verdichtergehäuse5 compressor housing
6 Ventilflansch6 valve flange
7 Verdichtereintritt7 Compressor entry
8 Flanschflächen8 flange surfaces
9 Verbindungskanal9 connecting channel
10 Ventilöffnung10 valve opening
11 Ventilsitz11 valve seat
12 Regelkanal12 control channel
13 Saugstutzen13 suction nozzles
14 Ausformkante14 forming edge
BF BezugsflächeBF reference surface
BF1 Parallelverschiebungen der Bezugsfläche BFBF 1 parallel displacements of the reference surface BF
AL TurboladerachseAL turbocharger axle
AK KanalachseAK duct axis
AVF Ventilflanschachse α, ß Winkel, vorzugsweise 12° bzw. 25" AVF valve flange axis α, ß angle, preferably 12 ° or 25 "

Claims

Ansprüche claims
1. Turbolader (1)1. Turbocharger (1)
mit einer Turbine (2); und mit einem mit der Turbine (2) über ein Lagergehäusewith a turbine (2); and one with the turbine (2) via a bearing housing
(4) verbundenen Verdichter (3), der ein Verdichtergehäuse (5) umfasst, das eine Bezugsfläche(4) connected compressor (3) comprising a compressor housing (5) having a reference surface
(BF) senkrecht zu einer Turboladerachse (AL) und einen mit einem Ventilsitz (11) versehenen Ventilflansch (6) für ein Schubumluftventil sowie einen Verbindungskanal(BF) perpendicular to a turbocharger axis (A L ) and provided with a valve seat (11) valve flange (6) for a diverter valve and a connecting channel
(9) zu einem Verdichtereintritt (7) aufweist, dadurch gekennzeichnet, dass der Ventilflansch (6) eine Flanschfläche (8) aufweist, die in einem Winkel (α) zur Bezugsfläche(9) to a compressor inlet (7), characterized in that the valve flange (6) has a flange surface (8) at an angle (α) to the reference surface
(BF) geneigt angeordnet ist, der wie folgt definiert ist: α = arctan ( (G-F) / (I-V) )(BF) is inclined, which is defined as follows: α = arctan ((G-F) / (I-V))
worinwherein
F: Abstand der Spiralquerschnittsmitte zu derF: distance of the spiral cross section center to the
Turboladerachse (AL) und G: der Abstand des Mittelpunktes der Ventilöffnung 10 zu der Turboladerachse AL I: der Abstand des Ventilflansches 6 zwischen derTurboladerachse (A L ) and G: the distance of the center of the valve opening 10 to the turbocharger axis A L I: the distance of the valve flange 6 between the
Bezugsseite bzw. der Bezugsfläche BF und demReference side or the reference surface BF and the
Mittelpunkt der Ventilöffnung 10; V: der Abstand des Schnittpunkts derCenter of the valve opening 10; V: the distance of the intersection of the
Ventilflanschachse AVF mit derValve flange axis A V F with the
Spiralquerschnittsmitte zu der Bezugsfläche BF ist, undSpiral cross-section center to the reference surface BF is, and
dass der Verbindungskanal (9) eine Kanalachse (Aκ) aufweist, die in einem Winkel (ß) geneigt angeordnet ist, der wie folgt definiert ist: I -(— •sinα) -Ein that the connecting channel (9) has a channel axis (A K ) which is inclined at an angle (β), which is defined as follows: I - (- • sinα) -E
P = arctan [ 1 ]P = arctan [1]
G+(—cos«)-RG + (- cos ") - R
worin:wherein:
A: der Innendurchmesser des Ventilflansches (6) ist,A: the inner diameter of the valve flange (6) is,
E: die Konturhöhe, gebildet aus Abstand von Bezugsfläche BF zu der Ebene der Schaufeleintrittskanten des Verdichterrades ist;E: the contour height formed from the distance from the reference surface BF to the plane of the blade leading edges of the compressor wheel;
R: der Abstand der Innenwand des Eintrittsstutzens 7 von der Turboladerachse AList.R: the distance of the inner wall of the inlet nozzle 7 from the turbocharger axis A L is.
2. Turbolader nach Anspruch 1, dadurch gekennzeichnet, dass die Winkel (α, ß) größer 0° sind.2. turbocharger according to claim 1, characterized in that the angles (α, ß) are greater than 0 °.
3. Turbolader nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Winkel (α, ß) spitze Winkel sind.3. turbocharger according to claim 1 or 2, characterized in that the angles (α, ß) are acute angles.
4. Turbolader nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Winkel (α) in einem Bereich von 0° bis 60° und der Winkel (ß) in einem Bereich von 15° bis 60° liegt.4. Turbocharger according to one of claims 1 to 3, characterized in that the angle (α) in a range of 0 ° to 60 ° and the angle (ß) is in a range of 15 ° to 60 °.
5. Turbolader nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Winkel (α) ungefähr 12° beträgt und der Winkel (ß) ungefähr 25° beträgt.5. turbocharger according to one of claims 1 to 4, characterized in that the angle (α) is about 12 ° and the angle (ß) is about 25 °.
6. Turbolader nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Verdichtergehäuse (5) ein Druckgussgehäuse ist. ichtergehäuse (5) eines Turboladers (1)6. turbocharger according to one of claims 1 to 5, characterized in that the compressor housing (5) is a die-cast housing. Outer housing (5) of a turbocharger (1)
mit einer Bezugsflache (BF) senkrecht zu einerwith a reference surface (BF) perpendicular to one
Turboladerachse (AL) ; mit einem Ventilflansch (6) für ein Schubumluftventil; und mit einem Verbindungskanal (9) zu einemTurbocharger axle (A L ); a valve flange (6) for a diverter valve; and with a connection channel (9) to a
Verdichtereintritt (7), gekennzeichnet durch wenigstens eines der kennzeichnenden Merkmale derCompressor inlet (7), characterized by at least one of the characterizing features of
Ansprüche 1 bis 6. Claims 1 to 6.
EP07819253A 2006-11-09 2007-10-23 Turbocharger Withdrawn EP2079908A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006052944 2006-11-09
PCT/EP2007/009192 WO2008055588A1 (en) 2006-11-09 2007-10-23 Turbocharger

Publications (1)

Publication Number Publication Date
EP2079908A1 true EP2079908A1 (en) 2009-07-22

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ID=39066136

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Application Number Title Priority Date Filing Date
EP07819253A Withdrawn EP2079908A1 (en) 2006-11-09 2007-10-23 Turbocharger

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US (1) US8161745B2 (en)
EP (1) EP2079908A1 (en)
JP (1) JP5325786B2 (en)
KR (1) KR20090087879A (en)
CN (1) CN101529062A (en)
WO (1) WO2008055588A1 (en)

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JP2010509530A (en) 2010-03-25
JP5325786B2 (en) 2013-10-23
US20100047054A1 (en) 2010-02-25
US8161745B2 (en) 2012-04-24
WO2008055588A1 (en) 2008-05-15
KR20090087879A (en) 2009-08-18
CN101529062A (en) 2009-09-09

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