EP1489263B1 - Turbocharger shaft-hub connection - Google Patents

Turbocharger shaft-hub connection Download PDF

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Publication number
EP1489263B1
EP1489263B1 EP03405441A EP03405441A EP1489263B1 EP 1489263 B1 EP1489263 B1 EP 1489263B1 EP 03405441 A EP03405441 A EP 03405441A EP 03405441 A EP03405441 A EP 03405441A EP 1489263 B1 EP1489263 B1 EP 1489263B1
Authority
EP
European Patent Office
Prior art keywords
shaft
thread
compressor wheel
flanks
attachment
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.)
Expired - Fee Related
Application number
EP03405441A
Other languages
German (de)
French (fr)
Other versions
EP1489263A1 (en
Inventor
Josef Bättig
Alfred Mueller
Balz Flury
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.)
Accelleron Industries AG
Original Assignee
ABB Turbo Systems AG
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 ABB Turbo Systems AG filed Critical ABB Turbo Systems AG
Priority to EP03405441A priority Critical patent/EP1489263B1/en
Priority to DE50306502T priority patent/DE50306502D1/en
Priority to US10/861,360 priority patent/US6918723B2/en
Publication of EP1489263A1 publication Critical patent/EP1489263A1/en
Application granted granted Critical
Publication of EP1489263B1 publication Critical patent/EP1489263B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • 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
    • F05D2250/00—Geometry
    • F05D2250/20—Three-dimensional
    • F05D2250/23—Three-dimensional prismatic
    • F05D2250/232—Three-dimensional prismatic conical
    • 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
    • F05D2250/20—Three-dimensional
    • F05D2250/28—Three-dimensional patterned
    • F05D2250/281—Three-dimensional patterned threaded

Definitions

  • the invention relates to the field of shaft / hub connections.
  • Turbochargers to increase the performance of reciprocating engines include an engine exhaust driven turbine and a torque transmitting shaft connected to the turbine compressor.
  • Turbochargers for smaller engine outputs advantageously have a radial compressor made of aluminum without a central bore, as known from DE 44 44 082.
  • the compressor is releasably connected for manufacturing and maintenance reasons with the turbine shaft.
  • the compressor wheel is screwed either directly or via an intermediate sleeve made of steel or bronze on a stub shaft with a conventional thread.
  • At least one threaded, cylindrical or conical centering seat provides centering of the compressor wheel with respect to the shaft.
  • the compressor wheel is braced against an axial stop on the shaft.
  • the torque transmission takes place frictionally in the thread on the pressed together in the axial direction supporting thread flanks.
  • the supporting thread flanks are as steep as possible to the shaft axis, so that the biasing force can act substantially normal to the surface of the supporting thread flanks.
  • GB 826 136 discloses a thread arrangement in an optical device.
  • US 4,304,428 discloses a threaded connection for emergency retrieval of drilling tool by means of the threaded connection.
  • GB 241 211 discloses a general screw / nut connection.
  • the invention is therefore an object of the invention to provide a compound of the type mentioned, which allows an improved torque transmission with reduced axial preload.
  • a shaft with a shaft attachment by means of a thread, in which either a bore with an internal thread is embedded in the shaft attachment or in the shaft end, and the shaft or the shaft attachment has a corresponding, can be introduced into the threaded hole pin with an external thread, and an axial stop is arranged on the shaft and on the shaft attachment, the inner and the outer thread to the axis of shaft and shaft attachment towards flat, torque transmitting flanks, which frictionally by mutual rotation of shaft and shaft attachment, the interaction of the axial stops by means of radial pressure can be connected to each other.
  • the decisive for the torque transmission radial pressure is due to the flat angle between the load-bearing, with their large surfaces frictionally superimposed flanks and the axis correspondingly larger than in conventional threaded connections. Thereby, the axial biasing force between the two parts to be joined can be reduced accordingly.
  • the flat-shaped supporting flanks allow improved centering of shaft extension and shaft.
  • the shaft attachment is shown by way of example as a cylindrical counterpart corresponding in shape and size approximately to the shaft.
  • the shaft attachment is a wheel-shaped part, such as the compressor wheel of a turbocharger.
  • the shaft has an external thread in the region of the connection point.
  • the external thread is formed on the shaft end in the form of a threaded pin 10.
  • a corresponding bore 20 is inserted, which is equipped with an internal thread.
  • shaft and shaft attachment For the axial positioning of the shaft attachment with respect to the shaft, shaft and shaft attachment have an axial stop 11 and 21.
  • the two axial stops usually have parallel surfaces produced with high precision, thus contributing significantly to the concentricity of shaft attachment and shaft. Between Axial stops can, further parts be arranged, for example, as shown in the figure, a sealing or damping disc. 3
  • Fig. 2 shows a view of a guided along the shaft axis section through the inventive compound.
  • the two axial stops 11 and 21 are pressed together when screwing the shaft attachment to the shaft, whereby the shaft attachment is biased against the shaft.
  • the shaft attachment is usually a larger, made of a relatively soft material part, the expansion of the shaft attachment can be prevented by the threaded pin in the threaded connection by pushing a hard steel bushing 4 on the shaft attachment.
  • the special, inventive design of the thread is shown enlarged in Fig. 3.
  • the thread has bearing flanks 15 and 25 as well as production-related, unstressed flanks 16 and 26.
  • the supporting flanks 15 and 25 enclose with the axis A of the shaft and the shaft attachment a very shallow angle ⁇ .
  • the flank angle ⁇ is ideally 5 ° to 15 °. The flatter this angle ⁇ , the lower the axial preload force that can be transmitted through the thread to clamp the two parts to be joined, the shaft and the shaft attachment by means of the axial stops against each other.
  • the thread according to the invention is designed to run more smoothly, preferably three-pass. This results in a given flank angle less deep thread grooves and thus lower cross-sectional weakenings.
  • a 3-thread thread due to the 3-cyclic symmetry leads to an improved centering of the shaft attachment on the shaft.
  • the turn-up angle is massively reduced.
  • the flat formed bearing flanks bring a further improvement in the centering of the shaft attachment on the shaft.
  • the flat thread according to the invention has substantially larger fillet radii 17 and 27.
  • the thread according to the invention has virtually no notch effect and is considerably more resilient with respect to dynamic torque fluctuations than a conventional thread.
  • the thread as shown in the various figures, is a conical thread
  • the introduction of force improves compared with a cylindrical version, while the screw-on paths shorten.
  • Figures 4 to 7 show detailed detailed views of the shaft and the shaft attachment.
  • the views in the axial direction show the three-start threads.
  • the three threads are arranged offset by 120 °.
  • the arrangement of the threaded pin and the bore, or the outer and the inner thread can also be reversed, so that the shaft attachment a threaded pin is arranged and the corresponding hole is recessed in the shaft end.
  • the threaded pin does not need to be designed as a stub.
  • the external thread can be arranged in a middle region of a rod-shaped shaft, wherein the bore in the shaft attachment must be correspondingly deep or continuous for the threaded extension.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Technisches GebietTechnical area

Die Erfindung bezieht sich auf das Gebiet der Wellen-/Nabenverbindungen.The invention relates to the field of shaft / hub connections.

Sie betrifft die Verbindung einer Welle mit einem Wellenaufsatz mittels einem Gewinde gemäss dem Oberbegriff des Patentanspruchs 1. Sie betrifft ferner einen Turbolader, dessen Turbinenwelle mit dem Verdichterrad entsprechend verbunden ist.It relates to the connection of a shaft with a shaft attachment by means of a thread according to the preamble of claim 1. It further relates to a turbocharger whose turbine shaft is connected to the compressor wheel accordingly.

Stand der TechnikState of the art

Turbolader zur Leistungssteigerung von Hubkolbenmotoren umfassen eine durch Motorenabgase angetriebene Turbine und einen über eine drehmomentübertragende Welle mit der Turbine verbundenen Verdichter. Turbolader für kleinere Motorenleistungen weisen vorteilhaft einen Radialverdichter aus Aluminium ohne durchgehende Zentralbohrung auf, wie etwa aus DE 44 44 082 bekannt.Turbochargers to increase the performance of reciprocating engines include an engine exhaust driven turbine and a torque transmitting shaft connected to the turbine compressor. Turbochargers for smaller engine outputs advantageously have a radial compressor made of aluminum without a central bore, as known from DE 44 44 082.

Das Verdichterrad ist dabei aus Herstellungs- und Wartungsgründen lösbar mit der Turbinenwelle verbunden.The compressor is releasably connected for manufacturing and maintenance reasons with the turbine shaft.

Bei den bekannten Lösungen wird das Verdichterrad entweder direkt oder über eine Zwischenbüchse aus Stahl oder Bronze auf einen Wellenstummel mit einem konventionellen Gewinde aufgeschraubt. Mindestens ein zum Gewinde versetzter, zylindrischer oder konischer Zentriersitz sorgt für die Zentrierung des Verdichterrades bezüglich der Welle.In the known solutions, the compressor wheel is screwed either directly or via an intermediate sleeve made of steel or bronze on a stub shaft with a conventional thread. At least one threaded, cylindrical or conical centering seat provides centering of the compressor wheel with respect to the shaft.

Bei einer solchen Wellen-/ Verdichterradverbindung wird das Verdichterrad gegen einen axialen Anschlag an der Welle verspannt. Die Drehmomentübertragung erfolgt im Gewinde reibschlüssig über die in axialer Richtung aneinandergepressten tragenden Gewindeflanken. Bei herkömmlichen Gewinden stehen die tragenden Gewindeflanken in einem möglichst steilen Winkel zur Wellenachse, damit die Vorspannkraft im wesentlichen normal zur Oberfläche der tragenden Gewindeflanken wirken kann.In such a shaft / compressor wheel connection, the compressor wheel is braced against an axial stop on the shaft. The torque transmission takes place frictionally in the thread on the pressed together in the axial direction supporting thread flanks. In conventional threads, the supporting thread flanks are as steep as possible to the shaft axis, so that the biasing force can act substantially normal to the surface of the supporting thread flanks.

Jüngste Leistungssteigerungen der Verdichter von Turbolader machen eine verbesserte Drehmomentübertragung von Welle auf Verdichterrad notwendig. Bei herkömmlichen Verbindungen bedeutet dies, dass die Vorspannkraft erhöht werden muss, um die tragenden Flanken der Gewinde in axialer Richtung stärker aneinander zu pressen. Dies führt jedoch zu einer reduzierten Fügestellendämpfung zwischen den miteinander verbundenen Teilen. Weiter einschränkend ist zudem die bei herkömmlichen Gewinden durch den Querschnittssprung von Gewindegang zu Gewindegang hervorgerufene Kerbwirkung.Recent increases in turbocharger compressor output require improved torque transmission from shaft to compressor wheel. In conventional connections, this means that the biasing force must be increased in order to press the supporting flanks of the threads in the axial direction more strongly against each other. However, this leads to a reduced joint damping between the interconnected parts. Further restricting is also the notch effect caused by the cross-sectional jump from thread to thread in conventional threads.

Aus anderen Anwendungsgebieten sind verschiedene Arten von Gewinden mit unterschiedlich steilen Gewindeflanken bekannt: GB 826 136 offenbart eine Gewindeanordnung in einem optischen Gerät. US 4,304,428 offenbart eine Gewindeverbindung, zur notfallmässigen Bergung von Bohrwerkzeug mittels der Gewindeverbindung. GB 241 211 offenbart eine allgemeine Schrauben-/ Mutterverbindung.From other fields of application, different types of threads with differently steep thread flanks are known: GB 826 136 discloses a thread arrangement in an optical device. US 4,304,428 discloses a threaded connection for emergency retrieval of drilling tool by means of the threaded connection. GB 241 211 discloses a general screw / nut connection.

Kurze Darstellung der ErfindungBrief description of the invention

Der Erfindung liegt folglich die Aufgabe zugrunde, eine Verbindung der eingangs genannten art zu schaffen, welche eine verbesserte Drehmomentübertragung bei reduzierter axialen Vorspannung ermöglicht.The invention is therefore an object of the invention to provide a compound of the type mentioned, which allows an improved torque transmission with reduced axial preload.

Erfindungsgemäss wird diese Aufgabe mit den Merkmalen des Patentanspruchs 1 gelöst.According to the invention, this object is achieved with the features of patent claim 1.

Bei der erfindungsgemässen Verbindung einer Welle mit einem Wellenaufsatz mittels einem Gewinde, bei welcher entweder in den Wellenaufsatz oder in das Wellenende eine Bohrung mit einem Innengewinde eingelassen ist, und die Welle oder der Wellenaufsatz einen entsprechenden, in die Gewindebohrung einbringbaren Zapfen mit einem Aussengewinde aufweist, und an der Welle und am Wellenaufsatz jeweils ein Axialanschlag angeordnet ist, weisen das Innen- und das Aussengewinde zur Achse von Welle und Wellenaufsatz hin flache, drehmomentübertragende Flanken auf, welche durch gegenseitige Verdrehung von Welle und Wellenaufsatz, unter Zusammenwirkung der Axialanschläge mittels radialer Pressung reibschlüssig miteinander verbindbar sind.In the inventive connection of a shaft with a shaft attachment by means of a thread, in which either a bore with an internal thread is embedded in the shaft attachment or in the shaft end, and the shaft or the shaft attachment has a corresponding, can be introduced into the threaded hole pin with an external thread, and an axial stop is arranged on the shaft and on the shaft attachment, the inner and the outer thread to the axis of shaft and shaft attachment towards flat, torque transmitting flanks, which frictionally by mutual rotation of shaft and shaft attachment, the interaction of the axial stops by means of radial pressure can be connected to each other.

Die für die Drehmomentübertragung entscheidende radiale Pressung ist dank dem flachen Winkel zwischen den tragenden, mit ihren grossen Oberflächen reibschlüssig aufeinanderliegenden Flanken und der Achse entsprechend grösser als bei herkömmlichen Gewindeverbindungen. Dadurch kann die axiale Vorspannkraft zwischen den beiden zu verbindenden Teilen entsprechend reduziert werden.The decisive for the torque transmission radial pressure is due to the flat angle between the load-bearing, with their large surfaces frictionally superimposed flanks and the axis correspondingly larger than in conventional threaded connections. Thereby, the axial biasing force between the two parts to be joined can be reduced accordingly.

Zudem ermöglichen die flach ausgebildeten tragenden Flanken ein verbessertes Zentrieren von Wellenaufsatz und Welle.In addition, the flat-shaped supporting flanks allow improved centering of shaft extension and shaft.

Weitere Vorteile ergeben sich aus den abhängigen Ansprüchen.Further advantages emerge from the dependent claims.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Im folgenden ist anhand der Figuren ein Ausführungsbeispiel der erfindungsgemässen Verbindung schematisch dargestellt und näher erläutert. In allen Figuren sind gleichwirkende Elemente mit gleichen Bezugszeichen versehen. Es zeigen:

Fig. 1
eine Ansicht auf eine Welle mit einem Wellenaufsatz mit einer erfindungsgemässen Verbindung,
Fig. 2
eine Ansicht auf einen entlang der Wellenachse geführten Schnitt durch die Verbindung nach Fig. 1,
Fig. 3
einen vergrössert dargestellten Ausschnitt III- III der Verbindung nach Fig. 2,
Fig. 4
eine Ansicht in Achsrichtung auf die Welle nach Fig. 1,
Fig. 5
eine Ansicht senkrecht zur Achse auf die Welle nach Fig. 1,
Fig. 6
eine Ansicht in Achsrichtung auf den Wellenaufsatz nach Fig. 1, und
Fig. 7
eine Ansicht auf einen entlang VII-VII geführten Schnitt durch den Wellenaufsatz nach Fig. 6,
In the following an embodiment of the inventive compound is schematically illustrated and explained in more detail with reference to FIGS. In all figures, the same elements are provided with the same reference numerals. Show it:
Fig. 1
a view of a shaft with a wave attachment with a compound according to the invention,
Fig. 2
a view of a guided along the shaft axis section through the compound of Fig. 1,
Fig. 3
an enlarged section III-III of the compound of Fig. 2,
Fig. 4
a view in the axial direction of the shaft of Fig. 1,
Fig. 5
a view perpendicular to the axis of the shaft of FIG. 1,
Fig. 6
a view in the axial direction of the shaft attachment of Fig. 1, and
Fig. 7
a view of a guided along VII-VII section through the wave tower of FIG. 6,

Weg zur Ausführung der ErfindungWay to carry out the invention

Fig. 1 zeigt eine Welle 1 und einen erfindungsgemäss mit der Welle verbundenen Wellenaufsatz 2. Der Wellenaufsatz ist beispielhaft als ein in Form und Grösse etwa der Welle entsprechendes, zylindrisches Gegenstück abgebildet. In der Regel handelt es sich beim Wellenaufsatz um ein radförmiges Teil, wie etwa das Verdichterrad eines Turboladers.1 shows a shaft 1 and a shaft attachment 2 connected to the shaft according to the invention. The shaft attachment is shown by way of example as a cylindrical counterpart corresponding in shape and size approximately to the shaft. In general, the shaft attachment is a wheel-shaped part, such as the compressor wheel of a turbocharger.

Die Welle weist im Bereich der Verbindungsstelle ein Aussengewinde auf. In der dargestellten Ausführungsform ist das Aussengewinde am Wellenende in Form eines Gewindezapfens 10 ausgebildet ist. In den Wellenaufsatz ist eine entsprechende Bohrung 20 eingelassen, welche mit einem Innengewinde ausgestattet ist.The shaft has an external thread in the region of the connection point. In the illustrated embodiment, the external thread is formed on the shaft end in the form of a threaded pin 10. In the shaft attachment a corresponding bore 20 is inserted, which is equipped with an internal thread.

Zur axialen Positionierung des Wellenaufsatzes bezüglich der Welle weisen Welle und Wellenaufsatz einen Axialanschlag 11 und 21 auf. Die beiden Axialanschläge haben in der Regel mit hoher Präzision gefertigte zueinander parallele Oberflächen, womit sie wesentlich zum Rundlauf von Wellenaufsatz und Welle beitragen. Zwischen den Axialanschlägen können, weitere Teile angeordnet sein, beispielsweise wie in der Figur dargestellt eine Dicht- oder Dämpfungsscheibe 3.For the axial positioning of the shaft attachment with respect to the shaft, shaft and shaft attachment have an axial stop 11 and 21. The two axial stops usually have parallel surfaces produced with high precision, thus contributing significantly to the concentricity of shaft attachment and shaft. Between Axial stops can, further parts be arranged, for example, as shown in the figure, a sealing or damping disc. 3

Fig. 2 zeigt eine Ansicht eines entlang der Wellenachse geführten Schnittes durch die erfindungsgemässe Verbindung. Die beiden Axialanschläge 11 und 21 werden beim Aufschrauben des Wellenaufsatzes auf die Welle zusammengepresst, wodurch der Wellenaufsatz gegen die Welle vorgespannt wird.Fig. 2 shows a view of a guided along the shaft axis section through the inventive compound. The two axial stops 11 and 21 are pressed together when screwing the shaft attachment to the shaft, whereby the shaft attachment is biased against the shaft.

Da es sich beim Wellenaufsatz in der Regel um ein grösseres, aus einem relativ weichen Material gefertigtes Teil handelt, kann im Bereich der Gewindeverbindung durch das Aufschieben einer harten Stahlbüchse 4 auf den Wellenaufsatz die Ausdehnung des Wellenaufsatzes durch den Gewindezapfen verhindert werden.Since the shaft attachment is usually a larger, made of a relatively soft material part, the expansion of the shaft attachment can be prevented by the threaded pin in the threaded connection by pushing a hard steel bushing 4 on the shaft attachment.

Die spezielle, erfindungsgemässe Gestaltung des Gewindes ist in Fig. 3 vergrössert dargestellt. Das Gewinde weist tragende Flanken 15 und 25 sowie herstellungsbedingte, nicht belastete Flanken 16 und 26 auf. Die tragenden Flanken 15 und 25 umschliessen mit der Achse A der Welle und des Wellenaufsatzes einen sehr flachen Winkel α. Der Flankenwinkel α beträgt idealerweise 5° bis 15°. Je flacher dieser Winkel α, desto geringer ist die axiale Vorspannkraft, welche durch das Gewinde übertragen werden kann, um die beiden zu verbindenden Teile, die Welle und den Wellenaufsatz mit Hilfe der Axialanschläge gegeneinander zu verspannen.The special, inventive design of the thread is shown enlarged in Fig. 3. The thread has bearing flanks 15 and 25 as well as production-related, unstressed flanks 16 and 26. The supporting flanks 15 and 25 enclose with the axis A of the shaft and the shaft attachment a very shallow angle α. The flank angle α is ideally 5 ° to 15 °. The flatter this angle α, the lower the axial preload force that can be transmitted through the thread to clamp the two parts to be joined, the shaft and the shaft attachment by means of the axial stops against each other.

Dagegen ist die für die Drehmomentübertragung entscheidende radiale Pressung bei einem flachen Winkel zwischen den tragenden Flanken und der Achse entsprechend grösser. Die tragenden Flanken liegen mit ihren grossen Oberflächen reibschlüssig aufeinander auf.In contrast, the decisive for the torque transmission radial pressure at a shallow angle between the supporting flanks and the axis is correspondingly larger. The load-bearing flanks are frictionally engaged with each other with their large surfaces.

Zur weiteren Reduktion der Vorspannkraft wird das erfindungsgemässe Gewinde mehrgängig, vorzugsweise 3-gängig, ausgeführt. Dies ergibt bei gegebenem Flankenwinkel weniger tiefe Gewindefurchen und somit geringere Querschnittschwächungen. Zudem führt ein 3-gängiges Gewinde aufgrund der 3-fachzyklischen Symmetrie zu einer verbesserten Zentrierung des Wellenaufsatzes auf der Welle.For further reduction of the biasing force, the thread according to the invention is designed to run more smoothly, preferably three-pass. This results in a given flank angle less deep thread grooves and thus lower cross-sectional weakenings. In addition, a 3-thread thread due to the 3-cyclic symmetry leads to an improved centering of the shaft attachment on the shaft.

Im Weiteren wird durch den grösseren Steigungswinkel der Windungen des mehrgängigen Gewindes der Aufdrehwinkel massiv reduziert.Furthermore, due to the larger pitch angle of the turns of the multi-start thread, the turn-up angle is massively reduced.

Die flach ausgebildeten tragenden Flanken bringen eine weiter Verbesserung in der Zentrierung des Wellenaufsatzes auf der Welle.The flat formed bearing flanks bring a further improvement in the centering of the shaft attachment on the shaft.

Gegenüber herkömmlichen Gewinden weist das erfindungsgemässe Flachgewinde wesentlich grössere Ausrundungsradien 17 und 27 auf. Dadurch hat das erfindungsgemässe Gewinde praktisch keine Kerbwirkung und ist bezüglich dynamischen Drehmomentschwankungen wesentlich höher belastbar als ein herkömmliches Gewinde.Compared with conventional threads, the flat thread according to the invention has substantially larger fillet radii 17 and 27. As a result, the thread according to the invention has virtually no notch effect and is considerably more resilient with respect to dynamic torque fluctuations than a conventional thread.

Handelt es sich beim Gewinde, wie in den verschiedenen Figuren dargestellt, um ein konisches Gewinde verbessert sich gegenüber einer zylindrischen Ausführung die Krafteinleitung, während sich die Aufschraubwege verkürzen. Je steiler der Winkel β des Konus, desto kürzer sind die Aufschraubwege, da beim Aufschrauben bisweilen mehrere Gewindegänge übersprungen werden können.If the thread, as shown in the various figures, is a conical thread, the introduction of force improves compared with a cylindrical version, while the screw-on paths shorten. The steeper the angle β of the cone, the shorter are the screw-on paths, since several threads can sometimes be skipped when screwed on.

Figuren 4 bis 7 zeigen detaillierte Einzelansichten der Welle und des Wellenaufsatzes. Die Ansichten in Achsrichtung zeigen die dreigängigen Gewinde. Die drei Gewindegänge sind um je 120° versetzt angeordnet.Figures 4 to 7 show detailed detailed views of the shaft and the shaft attachment. The views in the axial direction show the three-start threads. The three threads are arranged offset by 120 °.

Die Anordnung des Gewindezapfens und der Bohrung, beziehungsweise des Aussen- und des Innengewindes kann auch vertauscht werden, so dass am Wellenaufsatz ein Gewindezapfen angeordnet ist und die entsprechende Bohrung in das Wellenende eingelassen ist.The arrangement of the threaded pin and the bore, or the outer and the inner thread can also be reversed, so that the shaft attachment a threaded pin is arranged and the corresponding hole is recessed in the shaft end.

Ferner braucht der Gewindezapfen nicht als Stummel ausgebildet zu sein. So kann etwa das Aussengewinde in einem Mittelbereich einer stangenförmigen Welle angeordnet sein, wobei für den Gewindefortsatz die Bohrung im Wellenaufsatz entsprechend tief, beziehungsweise durchgehend sein muss.Furthermore, the threaded pin does not need to be designed as a stub. For example, the external thread can be arranged in a middle region of a rod-shaped shaft, wherein the bore in the shaft attachment must be correspondingly deep or continuous for the threaded extension.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

AA
Achseaxis
αα
Flankenwinkelflank angle
ββ
Konuswinkel des GewindesCone angle of the thread
11
Welle, TurbinenwelleShaft, turbine shaft
1010
Gewindezapfenthreaded pin
1111
Wellenschultershaft shoulder
1515
Tragende Flanke (Aussengewinde)Supporting flank (external thread)
1616
Nichttragende Flanke (Aussengewinde)Non-bearing flank (external thread)
1717
Ausrundung (Aussengewinde)Rounding (external thread)
22
Wellenaufsatz, VerdichterradShaft attachment, compressor wheel
2020
Gewindebohrungthreaded hole
2121
Plananschlagbackstop
2525
Tragende Flanke (Innengewinde)Supporting flank (internal thread)
2626
Nichttragende Flanke (Innengewinde)Non-bearing flank (internal thread)
2727
Ausrundung (Innengewinde)Rounding (internal thread)
33
Zwischenkörper, DichtringIntermediate body, sealing ring
44
Stahlhülsesteel sleeve

Claims (4)

  1. Turbocharger, comprising a turbine wheel and a compressor wheel (2) connected to the turbine wheel via a shaft (1), the shaft (1) and the compressor wheel (2) being connected by means of a thread, a bore (20) with an internal thread being incorporated either in the compressor wheel (2) or an end of the shaft(1) which is to be connected to the compressor wheel, and the shaft or the compressor wheel having a corresponding stem (10) which can be introduced into the threaded bore and has an external thread, and an axial stop (11, 21) being arranged in each case on the shaft (1) and on the compressor wheel (2), characterized in that the internal and external threads have torque-transmitting flanks (15, 25) which are flat toward the axis of shaft and compressor wheel (A) and which can be connected to one another frictionally by means of radial pressure by mutual rotation of shaft (1) and compressor wheel (2) with interaction between the axial stops.
  2. Turbocharger according to Claim 1, characterized in that the threaded stem (10) and the threaded bore (20) are designed to be at least partly conical, and in that the thread is a conical thread.
  3. Turbocharger according to either of Claims 1 and 2, characterized in that the thread is a multiple-start, in particular a three-start, thread.
  4. Turbocharger according to one of Claims 1 to 3, characterized in that the torque-transmitting flanks (15, 25) form an angle of between 5° and 15° with the axis of shaft and compressor wheel (A).
EP03405441A 2003-06-19 2003-06-19 Turbocharger shaft-hub connection Expired - Fee Related EP1489263B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP03405441A EP1489263B1 (en) 2003-06-19 2003-06-19 Turbocharger shaft-hub connection
DE50306502T DE50306502D1 (en) 2003-06-19 2003-06-19 Shaft / hub connection of a turbocharger
US10/861,360 US6918723B2 (en) 2003-06-19 2004-06-07 Shaft/hub connection

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03405441A EP1489263B1 (en) 2003-06-19 2003-06-19 Turbocharger shaft-hub connection

Publications (2)

Publication Number Publication Date
EP1489263A1 EP1489263A1 (en) 2004-12-22
EP1489263B1 true EP1489263B1 (en) 2007-02-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03405441A Expired - Fee Related EP1489263B1 (en) 2003-06-19 2003-06-19 Turbocharger shaft-hub connection

Country Status (3)

Country Link
US (1) US6918723B2 (en)
EP (1) EP1489263B1 (en)
DE (1) DE50306502D1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005030382A (en) * 2003-06-18 2005-02-03 Komatsu Ltd Compressor of turbomachinery and its compressor impeller
US20070009340A1 (en) * 2005-07-11 2007-01-11 Van Cor Dale E Conic threaded fastener and fastener system
NL2001433C2 (en) * 2008-04-02 2009-10-05 Bronswerk Heat Transfer Bv Conical screw coupling.
DE102011051961A1 (en) * 2011-07-20 2013-01-24 Zf Lenksysteme Gmbh Device for securing a unit
CN203306224U (en) * 2013-05-31 2013-11-27 深圳市大疆创新科技有限公司 Propeller and aircraft provided with same
DE102013015563A1 (en) * 2013-09-20 2015-03-26 Abb Turbo Systems Ag turbocharger
DE102013018005A1 (en) 2013-11-29 2015-06-03 Mtu Friedrichshafen Gmbh Shaft-hub connection
CN103846613B (en) * 2014-02-12 2016-06-15 中国北方发动机研究所(天津) The tapered tread method of attachment of booster turbine impeller and rotating shaft and attachment structure
US9889509B2 (en) * 2014-05-05 2018-02-13 Kennametal Inc. Cutter heads with improved coupling
US11097839B2 (en) * 2019-10-09 2021-08-24 Kitty Hawk Corporation Hybrid power systems for different modes of flight

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Publication number Priority date Publication date Assignee Title
GB241211A (en) * 1924-10-09 1927-01-10 Fr De Filetage Indesserrable D An improved self-locking nut and bolt
FR1140284A (en) * 1955-02-08 1957-07-18 Voigtlaender Ag Thread for optical devices, in particular for photographic lenses
FR2315568A1 (en) * 1975-06-25 1977-01-21 Vape Sa Ets SCREW FIXING DEVICE IN A CONSTRUCTION ELEMENT IN AGGLOMERATED MATERIAL
US4304428A (en) * 1976-05-03 1981-12-08 Grigorian Samvel S Tapered screw joint and device for emergency recovery of boring tool from borehole with the use of said joint
US4309135A (en) * 1980-07-18 1982-01-05 Keystone Consolidated Industries, Inc. Concrete anchor
US4712955A (en) * 1985-05-14 1987-12-15 Rexnord Inc. Expandable fastener assembly
NO882384L (en) * 1988-05-31 1989-12-01 Kongsberg Offshore As DEVICE FOR TENSIONING CONNECTIONS.
DE4444082A1 (en) 1994-12-10 1996-06-13 Abb Management Ag Engine exhaust turbocharger

Also Published As

Publication number Publication date
DE50306502D1 (en) 2007-03-29
US20040258467A1 (en) 2004-12-23
US6918723B2 (en) 2005-07-19
EP1489263A1 (en) 2004-12-22

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