EP1489263B1 - Turbocharger shaft-hub connection - Google Patents
Turbocharger shaft-hub connection Download PDFInfo
- 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 - Lifetime
Links
- 230000003993 interaction Effects 0.000 claims description 2
- 150000001875 compounds Chemical class 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 5
- 229910000831 Steel Inorganic materials 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 229910000906 Bronze Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000010974 bronze Substances 0.000 description 1
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 239000007779 soft material Substances 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
Images
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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
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
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.
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
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.
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,
- 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,
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
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
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
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
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
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
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.
- 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)
- 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.
- 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.
- Turbocharger according to either of Claims 1 and 2, characterized in that the thread is a multiple-start, in particular a three-start, thread.
- 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).
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
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) |
Families Citing this family (11)
| 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 |
| JP7342250B2 (en) * | 2019-10-09 | 2023-09-11 | キティー・ホーク・コーポレーション | Hybrid power system for different flight modes |
| US20240239531A1 (en) * | 2022-08-09 | 2024-07-18 | Pete Bitar | Compact and Lightweight Drone Delivery Device called an ArcSpear Electric Jet Drone System Having an Electric Ducted Air Propulsion System and Being Relatively Difficult to Track in Flight |
Family Cites Families (8)
| 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 |
-
2003
- 2003-06-19 EP EP03405441A patent/EP1489263B1/en not_active Expired - Lifetime
- 2003-06-19 DE DE50306502T patent/DE50306502D1/en not_active Expired - Lifetime
-
2004
- 2004-06-07 US US10/861,360 patent/US6918723B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| EP1489263A1 (en) | 2004-12-22 |
| US20040258467A1 (en) | 2004-12-23 |
| DE50306502D1 (en) | 2007-03-29 |
| US6918723B2 (en) | 2005-07-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2188534B1 (en) | Rotor mounting | |
| DE102007037760B4 (en) | Piston / cylinder unit with a cylinder housing, a piston and a piston rod | |
| EP1902224B1 (en) | Prestressed shaft and hub connection having a perfect cone shape | |
| WO1996035885A1 (en) | Shaft fixture | |
| EP1489263B1 (en) | Turbocharger shaft-hub connection | |
| EP3017146A1 (en) | Rotor for a turbocharger device, turbocharger device having a rotor, and shaft for a rotor of said type | |
| DE102009039993A1 (en) | Transmission arrangement for crank-continuously variable transmission of motor vehicle, has drive shaft comprising independent and different individual parts, which are connected together in torque proof, centrical and axial manner | |
| EP2184525A1 (en) | Pipe joint with a pipe and method for producing a joining section of a pipe joint | |
| DE102013224191A1 (en) | Shaft-hub joint connection and method of making the same | |
| EP0318977B1 (en) | Tightening device | |
| DE102005054285B3 (en) | Hub-swivel arrangement with face gear and wheel bearing | |
| EP3219442B1 (en) | Drive element for transmitting a torque to a thread insert sleeve | |
| DE19860418B4 (en) | Device for changing the timing of gas exchange valves of an internal combustion engine, in particular camshaft adjusting device with impeller | |
| EP2614265B1 (en) | Shaft for transmission of torque | |
| DE102009025151B4 (en) | Mounting arrangement and method for mounting a flywheel or flywheel on a crankshaft of an internal combustion engine | |
| DE102013208163A1 (en) | Adapter for an output shaft of a gearbox | |
| EP1741953B1 (en) | Vibration damper with rebound stop spring element | |
| EP3384183B1 (en) | Planetary carrier for a transmission stage of a planetary transmission, and pre-tensioning method | |
| DE102018130895A1 (en) | Rotor for a wind turbine and process | |
| EP3819136B1 (en) | Wheel bearing unit for a motor vehicle and method for manufacturing a wheel bearing unit | |
| DE10162910B4 (en) | Clamping gap nut | |
| DE102014209169A1 (en) | Device for securing a tensioning element against unintentional release | |
| DE102015209641A1 (en) | Screw connection and rotor for an exhaust gas turbocharger | |
| DE102012214764B4 (en) | Fastening arrangement for connecting a camshaft adjuster with a camshaft end of a camshaft | |
| DE19961567A1 (en) | Hydraulic device for continuously variable cam shaft adjustment has between vanes of inner rotor cylindrical dish shaped pendulum head guides in which pendulum heads are swivel mounted whilst feet are in grooves of outer rotor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR |
|
| AX | Request for extension of the european patent |
Extension state: AL LT LV MK |
|
| 17P | Request for examination filed |
Effective date: 20050608 |
|
| AKX | Designation fees paid |
Designated state(s): DE FR GB |
|
| RTI1 | Title (correction) |
Free format text: TURBOCHARGER SHAFT-HUB CONNECTION |
|
| GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
| GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
| REF | Corresponds to: |
Ref document number: 50306502 Country of ref document: DE Date of ref document: 20070329 Kind code of ref document: P |
|
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20070509 |
|
| ET | Fr: translation filed | ||
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed |
Effective date: 20071115 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20110630 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20110620 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20110622 Year of fee payment: 9 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20120619 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20130228 |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50306502 Country of ref document: DE Effective date: 20130101 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130101 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120619 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120702 |