EP1292779A1 - Dispositif dote d'un arbre et d'au moins un moyeu dispose sur cet arbre, et procede de fabrication de ce dispositif - Google Patents

Dispositif dote d'un arbre et d'au moins un moyeu dispose sur cet arbre, et procede de fabrication de ce dispositif

Info

Publication number
EP1292779A1
EP1292779A1 EP01931446A EP01931446A EP1292779A1 EP 1292779 A1 EP1292779 A1 EP 1292779A1 EP 01931446 A EP01931446 A EP 01931446A EP 01931446 A EP01931446 A EP 01931446A EP 1292779 A1 EP1292779 A1 EP 1292779A1
Authority
EP
European Patent Office
Prior art keywords
hub
shaft
opening
profile
cone
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP01931446A
Other languages
German (de)
English (en)
Inventor
Lukas Matt
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.)
ThyssenKrupp Technologies AG
Original Assignee
ThyssenKrupp Automotive 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 ThyssenKrupp Automotive AG filed Critical ThyssenKrupp Automotive AG
Publication of EP1292779A1 publication Critical patent/EP1292779A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F16D1/072—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving plastic deformation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/49—Member deformed in situ
    • Y10T403/4966—Deformation occurs simultaneously with assembly

Definitions

  • the invention relates to a device with a shaft and with at least one hub attached to this while and a method for producing this device.
  • a further disadvantage of the known constellation lies in the following: the highest voltage peaks in the hub occur directly at the end of the inlet cone. Since this end of the inlet cone lies on the edge area of the one hub face surface, edge defects of the hub (for example, forging errors or hardness errors on the hub edge) cracks inevitably. The previously known construction is therefore unsuitable for highly stressed joint connections.
  • Another disadvantage is the lack of a positive connection between the hub and the shaft. Due to this disadvantage, the shaft-hub connection does not have sufficient fatigue strength.
  • WO 99/5740 also discloses a shaft-hub connection in which the shaft was enlarged in the outer region prior to joining by reshaping at the joint.
  • the hub inlet is not formed here by a phase with an internal transition edge, but by an opening profile that opens tangentially into the cylindrical hub opening. This construction cannot avoid the high stress peaks near the hub edge, which also leads to cracks in the edge area of the hub and thus to the failure of the shaft-hub connection.
  • the disclosed inlet radius does not transmit any torque in this construction either, and is only used for the shaping of the shaft surfaces.
  • the effective usable width of the hub is also significantly reduced by this radius
  • the object of the present invention is to make the entire hub width usable for a positive and frictional connection, to reduce the abrasive sliding wear during joining and thus to increase the follow-up stresses and at the same time to shift the joining stresses from the critical hub edge area to a non-critical hub area ,
  • Fig. 1 in a front view of a first embodiment of the hub of the present device, Fig. 2 in a vertical section aa the hub of Fig. 1, wherein the hub opening one has a frustoconical and a cylindrical section,
  • FIG. 3 is a front view of a second embodiment of the hub of the present device
  • Fig. 5 is a front view of a third embodiment of the hub of the present device.
  • the hub au3 Fig. 1 which is a section of a shaft in front of the
  • the present device comprises a shaft 1 (FIG. 8) and at least one hub 2 (FIGS. 1 to 7 and 9 to 11), which can be fastened on the shaft 1.
  • All of FIGS. 1 to 11 show geometrical relationships which are shown greatly enlarged in comparison to the real hub and shaft size. This representation only serves to better explain the features of the construction.
  • the shaft 1 and hub 2 are shown before the joining process.
  • the outer shape of the hub 2 can, depending on requirements, as a cam disk, gear wheel, crank arm, cylindrical disk. Circle eccentric or the like can be formed and the hub is made of hardened or unhardened steel, sintered steel, cast material, plastic or the like, depending on the application.
  • the shaft is preferably a welded, cold-drawn steel tube.
  • 1 and 2 show a first embodiment of the present hub 2. the width of which is limited by two mutually parallel side surfaces 4 and 41.
  • the side surfaces 4 and 41 are preferably at right angles to the central or symmetrical axis A of the hub opening 3.
  • the distance B between the mutually parallel side surfaces 4 and 41 defines the width B of the hub 2, which is connected to the shaft 1.
  • the width for example the running width of a cam, can be narrower or wider than the mounting width B of this cam on the shaft 1.
  • 1 to 6 show, for the sake of simplicity, the hub width B equal to the fastening width B over time 1. In this case, the distance B between the side surfaces 4 and 41 defines the fastening width and at the same time the hub width.
  • the hub opening 3 has a first section Z, which is cylindrical and which adjoins the second end face 41 of the hub at one end.
  • the hub opening 3 also has a second section K1, the course of which deviates from a cylindrical course and which adjoins the first end face 4 on one end the hub 2 connects Inside the hub 2, the two profiles mentioned merge.
  • the second profile K 1 is illustrated in FIGS. 1 and 2 by a straight surface line 5 of a truncated cone K1 (cone).
  • the straight surface lines 5, with a parallel to the hub axis A, form the cone generation alpha.
  • the straight surface lines 5 of the first truncated cone K1 form an edge E in section with the first side surface 4 of the hub 2.
  • the first profile Z is illustrated in FIGS.
  • edges E and F are circumferential, preferably circular edges.
  • the transition of the first profile K1 into the cylindrical section Z of the hub opening 3 is formed by an edge e. The highest tension peaks occur at this transition edge e, which, however, cannot cause hub tears by laying in the center of the hub.
  • FIG. 7 shows a hub identical to the hub 2 from FIG. 1, which is to be pressed onto the shaft 1 shown in FIG. 8 in the pressing direction P.
  • This shaft 1 can be designed as a solid shaft or as a tube.
  • the outer contour of the shaft 1 in its undeformed area is preferably cylindrical with the outer diameter w.
  • protruding shaft elevations R are created by plastic deformation of the shaft material, which have an outer diameter r.
  • 8 shows a possible embodiment of the shaft elevations R with circumferential closed grooves and elevations. It is also possible to produce circumferential but not closed grooves and elevations which have a pitch like a thread (not shown).
  • a variant embodiment be expedient, in which the wave elevations llensymmetrieachs ⁇ as axially to the W ⁇ extending teeth are formed (not shown).
  • a longitudinal press fit between shaft 1 and hub 2 can be achieved in that the diameter r of the shaft elevations R is chosen to be larger than the diameter d of the cylindrical section Z of the hub opening 3.
  • the hub 2 with the edge E with the diameter D is in front Pushing direction P pushed onto shaft 1.
  • ⁇ S is expedient if the hub can be moved freely or with little pressure along shaft 1 up to the start of rolling R.
  • the diameter d of the cylindrical section Z of the hub opening 3 corresponds approximately to the diameter w of the undeformed sections of the shaft 1 Tolerance specification of the two diameters d and w is achieved by choosing a clearance fit or a transition fit.
  • the protruding shaft elevations R on the shaft 1 are not sheared off by the edge E on the hub 2 while the hub 2 is being pressed on. This is achieved when the protruding shaft elevations R of the rolling are received by the truncated cone K1 in the first contact thereof.
  • the diameter D of the edge E of the hub 2 should therefore be greater than or equal to the diameter r of the elevations R on the shaft 1.
  • the length L (FIG. 2) of the inlet profile K1 corresponds approximately to half the hub width B. This important feature of the invention also achieves that only approximately half of the shaft elevations R are abrasively smoothed by the cylindrical section Z of the hub opening 3 during the longitudinal pressing. This brings a significant increase in the quality of the attachment of the hub 2 to the shaft 1.
  • this longitudinal section K1 of the hub 2 is clearly in the self-locking range. Until the end position of the hub 2 on the shaft 1 has been reached, the joining stresses in this hub section are continuously increased without being able to have a detrimental effect on the hub edge. For this reason, this hub section K1 contributes significantly to increasing the fatigue strength of the connection.
  • Rg. 1 the depth t of this recess is also included t equal to D minus d of the truncated cone K1 and a section of the jacket of a cylinder is preferably chosen for the geometric shape of the recess N.
  • the axis of symmetry S of this cylindrical recess N preferably runs parallel to the axis of symmetry A of the hub opening 3.
  • the wave elevations R (FIG. 8) are shaped by the cone K1 (FIG. 1) and at the same time a part of the wave elevations R is pressed into the recess N This results in a positive connection that extends practically over the entire hub width B.
  • the entire hub width B can thus be used for the attachment of the hub 2 to the shaft 1 and therefore there is no loss of effectively load-bearing attachment size of the hub 2.
  • the opening 3 by two successive, i.e. composite cone sections K1 and K2 is formed.
  • the designations in FIGS. 1 and 2 also apply analogously to FIGS. 3 and 4.
  • the cone generation angle Alpha 1 belongs to the first cone section K1 of the hub opening 3.
  • the cone generation angle Alpha 2 belongs to the second cone section K2 of the hub opening 3.
  • the respective cone generation angle Alpha 1 and Alpha 2 are preferably less than or equal to 5 degrees.
  • the transition e from the first cone K1 to the second cone K2 lies approximately in the middle of the hub width B.
  • the chip tips at the cone transition e are in turn effectively held away from the critical edge region of the hub 2.
  • the recess N also acts here as a positive connection between the shaft 1 and the hub 2 over the entire hub width B.
  • FIG. 5 and 6 show a hub 2, the inlet profile K 3 of which is formed by a curve which continuously and continuously merges into the cylindrical section Z of the hub opening 3.
  • an inner edge is avoided.
  • the maximum joining stresses occur at the transition area of curve K 3 to cylindrical section Z of bore 3 shown here, which guarantee a high fatigue strength of the shaft-hub connection but cannot cause cracks in hub 2.
  • the curve K 3 mentioned can be shaped, for example, as a circular arc or as another geometric short.
  • the recess N ensures a positive fit over the entire hub width B.
  • the entire hub width B can be used for the fastening.
  • the roll R becomes continuous while the hub 2 is being pushed on reshaped and thus the preload between the shaft 1 and the hub 2 continuously increased until the axial end position of the hub 2 was reached.
  • a significantly higher joining pressure is achieved in comparison to the cited prior art and a drop in tension of the first rolling tongues R, which are first formed, is prevented.
  • the overall quality of fastening of the shaft-hub connection is significantly increased.
  • FIGS. 9 to 11 show alternative execution geometries for the recess N.
  • two groove-shaped recesses N 1 and n N2 are made in the hub opening 3, which are at an angular distance of 120 degrees apart.
  • two recesses N 3 and N 4 are provided, each of which has the contour of a parabola.
  • Such recesses N 3 and N 4 are diametrically opposed to one another.
  • recesses with a non-circular profile can also be used.
  • Fig. 11 shows such an embodiment and arrangement of recesses N5, N 6 and N 7, which e.g. a sequence of tangential adjoining ⁇
  • Arcs (not shown) or a polygon profile. 11 shows such a polygon profile, which is superimposed on the profile K 1 with the two determining diameters d and D.
  • the hub opening 3, the profiles K 1 to K 3 and the recesses N to N7 can be inexpensively machined by turning and / or broaching.
  • the production of this internal hub geometry can also be made without cutting e.g. done by sintering.
  • the present device comprises a shaft 1 and a hub 2 mounted on this shaft 1.
  • the hub 2 has an opening 3 which has a composite profile in the direction of the axis A of the hub 2.
  • This profile comprises a cylinder-shaped section Z and a conical section K1.
  • the cone generation angle alpha of the cone Kl is less than 5 angular degrees or is equal to 5 angle degrees.
  • the transition ⁇ between the sections Z, K1 of the profile is located in the hub opening 3, specifically in the central region of the

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Toys (AREA)
  • Golf Clubs (AREA)

Abstract

L'invention concerne un arbre (1) et un moyeu (2) disposé sur cet arbre et doté d'une ouverture (3), qui, dans le sens de son axe (A), présente un profil composé. Ce profil comprend une partie cylindrique (Z) et une partie conique (K 1). L'angle alpha générateur du cône (K1) est égal ou inférieure à 5 degrés. La transition (e) entre les parties susmentionnées (Z, K1) du profil se trouve dans la l'ouverture (3) du moyeu, approximativement dans la zone médiane de la largeur (B) du moyeu.
EP01931446A 2000-06-06 2001-04-20 Dispositif dote d'un arbre et d'au moins un moyeu dispose sur cet arbre, et procede de fabrication de ce dispositif Withdrawn EP1292779A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10027517A DE10027517A1 (de) 2000-06-06 2000-06-06 Einrichtung mit einer Welle und mit zumindest einer auf dieser Welle angebrachten Nabe und Verfahren für die Herstellung dieser Einrichtung
DE10027517 2000-06-06
PCT/DE2001/001525 WO2001094802A1 (fr) 2000-06-06 2001-04-20 Dispositif dote d"un arbre et d"au moins un moyeu dispose sur cet arbre, et procede de fabrication de ce dispositif

Publications (1)

Publication Number Publication Date
EP1292779A1 true EP1292779A1 (fr) 2003-03-19

Family

ID=7644557

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01931446A Withdrawn EP1292779A1 (fr) 2000-06-06 2001-04-20 Dispositif dote d'un arbre et d'au moins un moyeu dispose sur cet arbre, et procede de fabrication de ce dispositif

Country Status (9)

Country Link
US (1) US20030165354A1 (fr)
EP (1) EP1292779A1 (fr)
JP (1) JP2003536031A (fr)
KR (1) KR20030011823A (fr)
AU (1) AU2001258217A1 (fr)
DE (2) DE10027517A1 (fr)
HU (1) HUP0204380A2 (fr)
PL (1) PL358888A1 (fr)
WO (1) WO2001094802A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1387102A1 (fr) 2002-07-31 2004-02-04 Robert Bürgler Joint arbre-moyeu à pression
DE10334690B4 (de) * 2003-07-30 2008-08-21 Böckmann-Hannibal, Angela, Dipl.-Ing. (FH) Einrichtung zur Nockenwellenverstellung für Verbrennungskraftmaschinen
DE202007004553U1 (de) * 2007-03-28 2008-08-07 Mafell Ag Werkstückzentrierung
DE102007062595A1 (de) 2007-12-22 2009-07-02 Daimler Ag Nabe-Welle-Verbindung
US9181984B2 (en) * 2008-01-31 2015-11-10 Trane International Inc. Alignment feature for hub and driveshaft assembly
SE532046C2 (sv) * 2008-05-12 2009-10-13 Iba Hb Förband för momentöverföring mellan en axel och ett på axeln anbringat element
DE102010046619A1 (de) * 2010-09-25 2012-03-29 Bayerische Motoren Werke Aktiengesellschaft Rotor für einen Nockenwellenversteller und Nockenwellenverstellsystem
DE102014109818A1 (de) * 2014-07-14 2016-01-14 Thyssenkrupp Presta Teccenter Ag Gebaute Kurbelwelle mit in Kurbelwangen eingepressten Lagerzapfen

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US2082379A (en) * 1934-04-11 1937-06-01 Gen Motors Corp Press fitting
US2279956A (en) * 1941-06-20 1942-04-14 Harry E Sipe Shafting connection
US3293740A (en) * 1964-06-16 1966-12-27 Black & Decker Mfg Co Method of producing a hole saw mandrel
BR8009064A (pt) * 1980-05-16 1982-04-13 Caterpillar Tractor Co Estria afilada e processo de producacao da mesma
US4343563A (en) * 1980-05-16 1982-08-10 Caterpillar Tractor Co. Tapered spline and method of manufacturing same
FR2544645B1 (fr) * 1983-04-20 1986-05-30 Cegedur Methode d'assemblage d'un element annulaire sur un tube metallique en aluminium ou un de ses alliages
CH670137A5 (de) * 1985-03-06 1989-05-12 Fischer Ag Georg Verfahren zur herstellung einer verbundnockenwelle.
JPH0229262Y2 (fr) * 1986-09-30 1990-08-06
JPH0672616B2 (ja) * 1987-04-21 1994-09-14 株式会社ゼクセル 鋼シャフト複合アルミニウム合金ローター
DE69104016T3 (de) * 1990-11-19 1999-09-02 Nippon Piston Ring Co Ltd Maschinenelement mit mindestens einem mit Druck auf einer Welle befestigten Verbindungsteil.
DE4121951C1 (fr) * 1991-07-03 1992-12-24 Supervis Ets
JP3052037B2 (ja) * 1993-07-22 2000-06-12 本田技研工業株式会社 スプライン結合構造
JPH08121120A (ja) * 1994-08-31 1996-05-14 Nippon Piston Ring Co Ltd シャフトを嵌合部材に圧入してなる機械要素
WO1999057450A1 (fr) 1998-05-04 1999-11-11 Lukas Matt Dispositif comportant un arbre pourvu d'au moins un moyeu, ainsi que procede pour la fabrication de ce dispositif
DE19925028A1 (de) * 1999-06-01 2000-12-21 Thyssen Krupp Automotive Ag Nocken für zusammengesetzte Nockenwelle

Non-Patent Citations (1)

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Title
See references of WO0194802A1 *

Also Published As

Publication number Publication date
WO2001094802A1 (fr) 2001-12-13
PL358888A1 (en) 2004-08-23
US20030165354A1 (en) 2003-09-04
KR20030011823A (ko) 2003-02-11
DE10027517A1 (de) 2001-12-13
JP2003536031A (ja) 2003-12-02
AU2001258217A1 (en) 2001-12-17
DE10192365D2 (de) 2003-05-22
HUP0204380A2 (en) 2003-04-28

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