EP1489263A1 - Shaft-hub connection - Google Patents

Shaft-hub connection Download PDF

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Publication number
EP1489263A1
EP1489263A1 EP03405441A EP03405441A EP1489263A1 EP 1489263 A1 EP1489263 A1 EP 1489263A1 EP 03405441 A EP03405441 A EP 03405441A EP 03405441 A EP03405441 A EP 03405441A EP 1489263 A1 EP1489263 A1 EP 1489263A1
Authority
EP
European Patent Office
Prior art keywords
shaft
thread
attachment
shaft attachment
axis
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.)
Granted
Application number
EP03405441A
Other languages
German (de)
French (fr)
Other versions
EP1489263B1 (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 DE50306502T priority Critical patent/DE50306502D1/en
Priority to EP03405441A priority patent/EP1489263B1/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 - Lifetime 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 a through Engine exhaust driven turbine and one via a torque transmitting Compressor shaft connected to the turbine.
  • Turbocharger for smaller engine outputs advantageously have a radial compressor made of aluminum without continuous Central bore on, as known from DE 44 44 082.
  • the compressor wheel can be solved for manufacturing and maintenance reasons with the Turbine shaft connected.
  • the compressor wheel is either directly or via a Intermediate sleeve made of steel or bronze on a stub shaft with a conventional thread screwed on. At least one offset to the thread Cylindrical or conical centering seat ensures the centering of the compressor wheel regarding the wave.
  • the invention is therefore based on the object, a connection of the beginning to create the type mentioned, which with improved torque transmission allows reduced axial preload.
  • the radial pressure that is decisive for torque transmission is thanks to the flat Angle between the load-bearing, with their large surfaces friction flanks lying on top of each other and the axis correspondingly larger than at conventional threaded connections. This allows the axial preload between the two parts to be connected are reduced accordingly.
  • the flat-shaped supporting flanks enable an improved Centering the shaft attachment and shaft.
  • the shaft attachment is exemplary as one in shape and size approximately Corresponding cylindrical counterpart shown. As a rule, it is in the shaft attachment around a wheel-shaped part, such as the compressor wheel Turbocharger.
  • the shaft has an external thread in the area of the connection point.
  • the external thread at the shaft end in the form of a Threaded pin 10 is formed.
  • the shaft and Shaft attachment For the axial positioning of the shaft attachment with respect to the shaft, the shaft and Shaft attachment an axial stop 11 and 21.
  • the two axial stops have in the Usually with high precision manufactured parallel surfaces, with which they make a significant contribution to the concentricity of the shaft attachment and shaft. Between Axial stops, further parts can be arranged, for example as in the figure shown a sealing or damping disc 3rd
  • FIG. 2 shows a view of a section through the shaft axis compound according to the invention.
  • the two axial stops 11 and 12 are at Screwing the shaft attachment onto the shaft, which causes the Shaft attachment is biased against the shaft.
  • the shaft attachment is usually a larger one, made of a relatively soft one Material manufactured part can in the area of the threaded connection through the Sliding a hard steel sleeve 4 on the shaft extension of the Shaft attachment can be prevented by the threaded pin.
  • the special design of the thread according to the invention is enlarged in FIG. 3 shown.
  • the thread has load-bearing flanks 15 and 25 as well as manufacturing-related, edges 16 and 26 not loaded.
  • the supporting flanks 15 and 25 enclose with the axis A of the shaft and the shaft attachment a very flat angle ⁇ .
  • the Flank angle ⁇ is ideally 5 ° to 15 °, depending on the requirements of the Connection or the material of the parts to be connected, however, also in the range of 0 ° up to 45 ° or even 60 °.
  • the flatter this angle ⁇ the smaller it is axial preload, which can be transmitted through the thread to the two parts to be connected, the shaft and the shaft attachment using the axial stops to brace against each other.
  • the decisive radial pressure for torque transmission is corresponding to a flat angle between the supporting flanks and the axis greater.
  • the large flanks of the load-bearing flanks are friction-locked on each other.
  • the thread according to the invention is used to further reduce the pretensioning force Multi-course, preferably 3-course. Given a given Flank angle less deep thread grooves and therefore less Cross-sectional weaknesses. In addition, a 3-start thread leads due to the 3-fold cyclic Symmetry for an improved centering of the shaft attachment on the Wave.
  • the flat-shaped supporting flanks bring a further improvement in the Centering of the shaft attachment on the shaft.
  • the flat thread according to the invention has significantly larger fillet radii 17 and 27. That’s why Thread according to the invention has practically no notch effect and is dynamic Torque fluctuations are much more resilient than a conventional thread.
  • the thread as shown in the different figures, is a conical thread improves compared to a cylindrical version Force transmission while the screwing distances are shortened.
  • the steeper the angle ⁇ of the Cone the shorter the screw-on distances, since sometimes several are used when screwing on Threads can be skipped.
  • Figures 4 to 7 show detailed individual views of the shaft and the shaft attachment.
  • the Axial views show the three-start thread.
  • the three threads are arranged offset by 120 °.
  • the arrangement of the threaded pin and the bore, or the outer and of the internal thread can also be interchanged, so that on the shaft attachment Threaded pin is arranged and the corresponding hole in the shaft end is let in.
  • the threaded pin need not be designed as a stub.
  • the external thread can be arranged in a central region of a rod-shaped shaft, the bore in the shaft attachment being correspondingly deep for the thread extension, or must be continuous.

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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)

Abstract

The shaft (1) is connected to an impeller (2), with one having a bore (20) with internal thread, the other having a journal (10) with outer thread, and both having an axial stop (11,21). Both threads have flat torque-transmitting sides facing the axis (A) of shaft and impeller. Relative turning of shaft and impeller are brought into friction connection by radial pressure, via the axial stops. Journal and bore are at least partly of conical shape, and the tapered thread is a multiple esp. triple thread. Sides and axis of shaft and impeller enclose an angle smaller than 45[deg], esp. between 5[deg] and 15[deg]. The connection is for a turbocharger.

Description

Technisches GebietTechnical field

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 also 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 a through Engine exhaust driven turbine and one via a torque transmitting Compressor shaft connected to the turbine. Turbocharger for smaller engine outputs advantageously have a radial compressor made of aluminum without continuous Central bore on, as known from DE 44 44 082.

Das Verdichterrad ist dabei aus Herstellungs- und Wartungsgründen lösbar mit der Turbinenwelle verbunden.The compressor wheel can be solved for manufacturing and maintenance reasons with the Turbine shaft connected.

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 either directly or via a Intermediate sleeve made of steel or bronze on a stub shaft with a conventional thread screwed on. At least one offset to the thread Cylindrical or conical centering seat ensures the centering of the compressor wheel regarding the wave.

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. With such a shaft / compressor wheel connection, the compressor wheel is against one axial stop clamped on the shaft. The torque transmission takes place in the Threads frictionally over the load-bearing parts that are pressed together in the axial direction Thread flanks. With conventional threads, the load-bearing thread flanks are in an angle that is as steep as possible to the shaft axis, so that the prestressing force essentially can act 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 performance of turbocharger compressors make an improved one Torque transmission from shaft to compressor wheel necessary. With conventional This means that the pretension must be increased to the connections the flanks of the threads in the axial direction. This however leads to a reduced joint damping between the two connected parts. Another limitation is that of conventional threads caused by the cross-sectional jump from thread to thread Notch effect.

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 based on the object, a connection of the beginning to create the type mentioned, which with improved torque transmission allows 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.When connecting a shaft to a shaft attachment according to the invention by means of a thread in which either in the shaft attachment or in the shaft end Bore is embedded with an internal thread, and the shaft or the shaft attachment a corresponding pin that can be inserted into the threaded bore with a Has external thread, and each on the shaft and on the shaft attachment Axial stop is arranged, the internal and external threads to the axis of Shaft and shaft attachment towards flat, torque-transmitting flanks, which through mutual rotation of shaft and shaft attachment, in cooperation with the Axial stops can be frictionally connected to one another by means of radial pressure.

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 radial pressure that is decisive for torque transmission is thanks to the flat Angle between the load-bearing, with their large surfaces friction flanks lying on top of each other and the axis correspondingly larger than at conventional threaded connections. This allows the axial preload between the two parts to be connected are reduced accordingly.

Zudem ermöglichen die flach ausgebildeten tragenden Flanken ein verbessertes Zentrieren von Wellenaufsatz und Welle.In addition, the flat-shaped supporting flanks enable an improved Centering the shaft attachment and shaft.

Weitere Vorteile ergeben sich aus den abhängigen Ansprüchen. Further advantages result 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,
An exemplary embodiment of the connection according to the invention is shown schematically and explained in more detail below with reference to the figures. In all figures, elements with the same effect are provided with the same reference symbols. Show it:
Fig. 1
2 shows a view of a shaft with a shaft attachment with a connection according to the invention,
Fig. 2
2 shows a view of a section taken along the shaft axis through the connection according to FIG. 1,
Fig. 3
3 shows an enlarged section III-III of the connection according to FIG. 2,
Fig. 4
2 shows a view in the axial direction of the shaft according to FIG. 1,
Fig. 5
2 shows a view perpendicular to the axis of the shaft according to FIG. 1,
Fig. 6
a view in the axial direction of the shaft attachment of FIG. 1, and
Fig. 7
6 shows a view of a section taken along VII-VII through the shaft attachment according to FIG. 6,

Weg zur Ausführung der ErfindungWay of carrying 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 one connected to the shaft according to the invention Shaft attachment 2. The shaft attachment is exemplary as one in shape and size approximately Corresponding cylindrical counterpart shown. As a rule, it is in the shaft attachment around a wheel-shaped part, such as the compressor wheel 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 area of the connection point. In the The embodiment shown is the external thread at the shaft end in the form of a Threaded pin 10 is formed. There is a corresponding hole in the shaft attachment 20 embedded, 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, the shaft and Shaft attachment an axial stop 11 and 21. The two axial stops have in the Usually with high precision manufactured parallel surfaces, with which they make a significant contribution to the concentricity of the shaft attachment and shaft. Between Axial stops, further parts can be arranged, for example as in the figure shown a sealing or damping disc 3rd

Fig. 2 zeigt eine Ansicht eines entlang der Wellenachse geführten Schnittes durch die erfindungsgemässe Verbindung. Die beiden Axialanschläge 11 und 12 werden beim Aufschrauben des Wellenaufsatzes auf die Welle zusammengepresst, wodurch der Wellenaufsatz gegen die Welle vorgespannt wird.FIG. 2 shows a view of a section through the shaft axis compound according to the invention. The two axial stops 11 and 12 are at Screwing the shaft attachment onto the shaft, which causes 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 one, made of a relatively soft one Material manufactured part can in the area of the threaded connection through the Sliding a hard steel sleeve 4 on the shaft extension of the Shaft attachment can be prevented by the threaded pin.

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°, kann je nach Anforderung an die Verbindung oder dem Material der zu verbindenden Teile jedoch auch im Bereich von 0° bis 45° oder gar 60° ausgeführt werden. 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 design of the thread according to the invention is enlarged in FIG. 3 shown. The thread has load-bearing flanks 15 and 25 as well as manufacturing-related, edges 16 and 26 not loaded. The supporting flanks 15 and 25 enclose with the axis A of the shaft and the shaft attachment a very flat angle α. The Flank angle α is ideally 5 ° to 15 °, depending on the requirements of the Connection or the material of the parts to be connected, however, also in the range of 0 ° up to 45 ° or even 60 °. The flatter this angle α, the smaller it is axial preload, which can be transmitted through the thread to the two parts to be connected, the shaft and the shaft attachment using the axial stops to brace 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 radial pressure for torque transmission is corresponding to a flat angle between the supporting flanks and the axis greater. The large flanks of the load-bearing flanks are friction-locked on each other.

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.The thread according to the invention is used to further reduce the pretensioning force Multi-course, preferably 3-course. Given a given Flank angle less deep thread grooves and therefore less Cross-sectional weaknesses. In addition, a 3-start thread leads due to the 3-fold cyclic Symmetry for an improved centering of the shaft attachment on the Wave.

Im Weiteren wird durch den grösseren Steigungswinkel der Windungen des mehrgängigen Gewindes der Aufdrehwinkel massiv reduziert. Furthermore, the larger pitch angle of the turns of the multi-course Thread the opening angle massively reduced.

Die flach ausgebildeten tragenden Flanken bringen eine weiter Verbesserung in der Zentrierung des Wellenaufsatzes auf der Welle.The flat-shaped supporting 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 to conventional threads, the flat thread according to the invention has significantly larger fillet radii 17 and 27. That’s why Thread according to the invention has practically no notch effect and is dynamic Torque fluctuations are much more resilient 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 different figures, is a conical thread improves compared to a cylindrical version Force transmission while the screwing distances are shortened. The steeper the angle β of the Cone, the shorter the screw-on distances, since sometimes several are used when screwing on Threads can be skipped.

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 individual views of the shaft and the shaft attachment. The Axial views show the three-start thread. 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 of the internal thread can also be interchanged, so that on the shaft attachment Threaded pin is arranged and the corresponding hole in the shaft end is let in.

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 need not be designed as a stub. For example the external thread can be arranged in a central region of a rod-shaped shaft, the bore in the shaft attachment being correspondingly deep for the thread extension, or must be continuous.

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)Load-bearing flank (external thread)
1616
Nichttragende Flanke (Aussengewinde)Non-load-bearing flank (external thread)
1717
Ausrundung (Aussengewinde)Fillet (external thread)
22
Wellenaufsatz, VerdichterradShaft attachment, compressor wheel
2020
Gewindebohrungthreaded hole
2121
Plananschlagbackstop
2525
Tragende Flanke (Innengewinde)Load-bearing flank (internal thread)
2626
Nichttragende Flanke (Innengewinde)Non-load-bearing flank (internal thread)
2727
Ausrundung (Innengewinde)Fillet (internal thread)
33
Zwischenkörper, DichtringIntermediate body, sealing ring
44
Stahlhülsesteel sleeve

Claims (5)

Verbindung einer Welle (1) mit einem Wellenaufsatz (2) mittels einem Gewinde, wobei entweder in den Wellenaufsatz oder in das Wellenende eine Bohrung (20) mit einem Innengewinde eingelassen ist, und die Welle oder der Wellenaufsatz einen entsprechenden, in die Gewindebohrung einbringbaren Zapfen (10) mit einem Aussengewinde aufweist, und
an der Welle und am Wellenaufsatz jeweils ein Axialanschlag (11, 21) angeordnet ist, dadurch gekennzeichnet, dass
das Innen- und das Aussengewinde zur Achse von Welle und Wellenaufsatz (A) hin flache, drehmomentübertragende Flanken (15, 25) aufweisen, welche durch gegenseitige Verdrehung von Welle und Wellenaufsatz, unter Zusammenwirkung der Axialanschläge mittels radialer Pressung reibschlüssig miteinander verbindbar sind.Connection of a shaft (1) to a shaft attachment (2) by means of a thread, a bore (20) with an internal thread being inserted either in the shaft attachment or in the shaft end, and the shaft or the shaft attachment having a corresponding pin that can be inserted into the threaded bore (10) with an external thread, and
an axial stop (11, 21) is arranged on the shaft and on the shaft attachment, characterized in that
the internal and external threads have flat, torque-transmitting flanks (15, 25) towards the axis of the shaft and shaft attachment (A), which can be frictionally connected to one another by mutual rotation of the shaft and shaft attachment, in cooperation with the axial stops by means of radial pressure. Verbindung nach Anspruch 1, dadurch gekennzeichnet, dass der Gewindezapfen (10) und die Gewindebohrung (20) zumindest teilweise konusförmig ausgebildet sind, und dass es sich beim Gewinde um ein konisches Gewinde handelt.Connection according to claim 1, characterized in that the threaded pin (10) and the threaded bore (20) are at least partially conical, and that the thread is a conical thread. Verbindung nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass das Gewinde ein mehrgängiges, insbesondere ein dreigängiges, Gewinde ist.Connection according to one of claims 1 or 2, characterized in that the thread is a multi-start, in particular a three-start, thread. Verbindung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die drehmomentübertragenden Flanken (15, 25) mit der Achse von Welle und Wellenaufsatz einen Winkel kleiner als 45°, insbesondere zwischen 5° und 15° bilden.Connection according to one of Claims 1 to 3, characterized in that the torque-transmitting flanks (15, 25) form an angle of less than 45 °, in particular between 5 ° and 15 °, with the axis of the shaft and shaft attachment. Turbolader, umfassend ein Turbinenrad und ein über eine Welle mit dem Turbinenrad verbundenes Verdichterrad, wobei die Welle und das Verdichterrad mittels einer Verbindung gemäss einem der Ansprüche 1 bis 4 verbunden sind.Turbocharger, comprising a turbine wheel and a shaft with the turbine wheel connected compressor wheel, the shaft and the compressor wheel by means of a Connection according to one of claims 1 to 4 are connected.
EP03405441A 2003-06-19 2003-06-19 Turbocharger shaft-hub connection Expired - Lifetime EP1489263B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE50306502T DE50306502D1 (en) 2003-06-19 2003-06-19 Shaft / hub connection of a turbocharger
EP03405441A EP1489263B1 (en) 2003-06-19 2003-06-19 Turbocharger shaft-hub connection
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)

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

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ID=33396093

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03405441A Expired - Lifetime 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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CN103846613A (en) * 2014-02-12 2014-06-11 中国北方发动机研究所(天津) Connection method and connection structure of tapered threads of impeller and rotating shaft of turbine of supercharger

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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
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CN114375276A (en) * 2019-10-09 2022-04-19 小鹰公司 Short-distance take-off and landing carrier with forward swept wings
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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

Also Published As

Publication number Publication date
EP1489263B1 (en) 2007-02-14
US6918723B2 (en) 2005-07-19
US20040258467A1 (en) 2004-12-23
DE50306502D1 (en) 2007-03-29

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