WO2009098005A2 - Arbre et procédé de fabrication d'un arbre, en particulier pour un moteur de véhicule automobile - Google Patents

Arbre et procédé de fabrication d'un arbre, en particulier pour un moteur de véhicule automobile Download PDF

Info

Publication number
WO2009098005A2
WO2009098005A2 PCT/EP2009/000643 EP2009000643W WO2009098005A2 WO 2009098005 A2 WO2009098005 A2 WO 2009098005A2 EP 2009000643 W EP2009000643 W EP 2009000643W WO 2009098005 A2 WO2009098005 A2 WO 2009098005A2
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
bearing
storage area
axis
rotation
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.)
Ceased
Application number
PCT/EP2009/000643
Other languages
German (de)
English (en)
Other versions
WO2009098005A8 (fr
WO2009098005A3 (fr
Inventor
Ag Daimler
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.)
Mercedes Benz Group AG
Original Assignee
Daimler 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 Daimler AG filed Critical Daimler AG
Publication of WO2009098005A2 publication Critical patent/WO2009098005A2/fr
Publication of WO2009098005A3 publication Critical patent/WO2009098005A3/fr
Anticipated expiration legal-status Critical
Publication of WO2009098005A8 publication Critical patent/WO2009098005A8/fr
Ceased 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/264—Rotating balancer shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F01M2011/028—Arrangements of lubricant conduits for lubricating balance shafts
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/18—Camshafts
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/53—Spring-damper, e.g. gas springs
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts

Definitions

  • the invention relates to a shaft, in particular for an engine of a motor vehicle specified in the preamble of patent claim 1 and a method for producing a shaft specified in the preamble of claim 7 Art.
  • the shaft is formed as a cast balancing shaft of an engine of a motor vehicle and comprises two cylindrical bearing portions which extend along an axis of rotation of the shaft and relative to a circular cylindrical envelope surface each having an axial recess relative to the axis of rotation, whereby the shaft compared to conventional round profile shafts a lesser Owns weight.
  • the object of the present invention is to provide a shaft and a method for producing a shaft, which enable a further weight saving.
  • at least one recess in the bearing area is provided on the circumference of the shaft, which leads to a reduction of the cylindrical portion.
  • This allows, in addition to the weight savings achieved by this, an additional reduction of the friction power and accordingly lower storage temperatures during operation of the shaft.
  • lubricant-for example engine oil- made possible due to the radial recess, a higher lubricant film thickness reserve results, as a result of which the shaft has less wear and thus an increased service life.
  • Another aspect of the invention relates to a method for producing a shaft according to one of the preceding embodiments, wherein according to the invention at least a part of the shaft is produced by means of a forming process.
  • a forming process in addition, a significant reduction in unit costs.
  • waves are mass parts, so that there are additional cost advantages with correspondingly reduced unit costs. It has proven to be advantageous that a deep-drawing process and / or a hydroforming process is used as the forming process. This allows automated and rapid production even of complex shaft geometries, whereby waves with a reduced total weight and improved running properties can be produced quickly and inexpensively.
  • Fig. 1 is a perspective view of a formed as a balance shaft shaft according to the prior art
  • FIG. 2 shows a schematic sectional view of a bearing region of the shaft according to the sectional plane H-II shown in FIG. 1;
  • FIG. Fig. 3 is a schematic and partial side view of a
  • Fig. 4 is a schematic and partial side view of a
  • Fig. 5 is a schematic and partial side view of a
  • Fig. 6 is a schematic and frontal sectional view of a storage area of a shaft according to the invention according to a fourth embodiment.
  • the shaft in this case comprises two cylindrical bearing regions 10a 1, 10b which both extend along an axis of rotation A of the shaft and in each case comprise a recess 14a, 14b, which is axial with respect to the axis of rotation A, relative to a circular cylindrical enveloping surface 12 (see FIG.
  • FIG. 2 shows a schematic sectional view of the storage area 10a according to the sectional plane H-II shown in FIG. It can be seen in particular that the storage area 10a has a wrap angle of over 180 ° relative to the wrapping surface 12 in order to ensure reliable guidance and to make it impossible for the shaft to "drop" within its associated storage housing.
  • FIG. 3 shows a schematic and partial side view of the bearing area 10 of a shaft according to the invention in accordance with a first exemplary embodiment.
  • the shaft can optionally be designed as a balance shaft, camshaft or crankshaft.
  • the bearing region 10 in this case comprises two opposite the cladding surface 12 in relation to FIG on the rotation axis A radial recesses 18a, 18b, whereby an additional weight saving is achieved.
  • the storage area 10 thus has a variable storage width 16 over the circumference of the storage area 10.
  • the storage width 16 can vary by 60% and more over the circumference of the storage area 10.
  • the bearing region 10 has an open cross-sectional contour-as shown in FIG.
  • the radial recesses 18a, 18b are advantageously formed in a region of the bearing region 10, which is mechanically less loaded during operation of the shaft and extend in the present embodiment, along a lying outside the storage area 10 length range 20a, 20b of the shaft.
  • the radial recesses 18a, 18b are furthermore designed such that at least the bearing region 10 is mirror-symmetrical and has a mirror symmetry plane IH-III. This prevents tilting of the bearing area 10 within the motor housing due to undesired acceleration forces and ensures a correspondingly reliable and uniform operation of the shaft.
  • the shaft Due to the reduced friction surface of the bearing area 10, the shaft thus consumes a correspondingly lower friction power, which additionally results in lower storage temperatures during operation. This reduces wear and increases the life of the shaft according to the invention.
  • the radial recesses 18a, 18b also allow the formation of a Dispersg bines lubricant, whereby a higher lubricant film thickness reserve is ensured during the operation of the shaft and the lubrication is improved overall.
  • the shaft comprises a cavity 24 (see Fig. 6) which can be filled with the lubricant, for example engine oil, so that, on the one hand, a further reduction in weight is provided and, on the other hand, a further improvement in heat dissipation is achieved.
  • the shaft shown which is a mass part, is produced here by means of a hydroforming process at a pressure between about 2000 bar and 2500 bar from a steel sheet.
  • a hardenable alloy is preferably used here, at least in the bearing area 10, in order to ensure a correspondingly high longevity and operational reliability of the shaft.
  • this represents a quick, simple and cost-effective way to additionally form the fillable with the lubricant cavity 24 in one step.
  • the shaft is made by welding at least two, formed as deep-drawn parts
  • the bearing area 10 in addition to the radial recesses 18a, 18b additionally comprises three groove-shaped radial recesses 18c-e, which provide an additional volume for receiving the lubricant.
  • the bearing region 10 is not mirror-symmetrical in this case and, in addition to the radial recesses 18a, 18b, comprises five cross-shaped radial recesses 18c-g.
  • the recesses 18c-g each have a width and a depth of 1 mm and can be introduced, for example, inexpensively and fully automatically on a lathe by means of a thread turning process into the storage area 10. The pairwise distance of the recesses 18c-g can then be easily determined via the thread pitch 22.
  • the recesses 18c-g shown also provide for improved ventilation and increased delivery volume of the lubricant, which reduces the frictional losses of the shaft and increases the service life of the shaft.
  • the bearing region 10 has a closed contour, which comprises two radial recesses 18a, 18b in relation to the circumferential surface 12, which is circular in cross-section.
  • the bearing area 10 is thus similar to a cam of a known camshaft, but does not extend beyond the envelope surface 12 of the shaft.
  • the two recesses 18a, 18b also improve the lubricating film structure and "push" during operation of the shaft lubricant before him, so that there is also an additional lubricant delivery volume and improved lubrication.
  • the storage area 10 shown can alternatively be used as a cam, wherein by adaptation of the recesses 18a and 18b influence on a Anberichtweg or a Angular acceleration of a component to be actuated - for example, a gas exchange valve - can be taken.
  • the embodiment shown can also be combined with the preceding embodiments.
  • an embodiment of the shaft can be provided as duo or triple camshaft to allow, for example, different lifting curves of the component to be actuated.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Ocean & Marine Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

L'invention concerne un arbre, en particulier pour un moteur de véhicule automobile, comprenant au moins une zone d'appui (10) cylindrique, qui s'étend le long d'un axe de rotation (A) de l'arbre et comprend au moins un évidement axial (14) par rapport à l'axe de rotation (A) et à une surface enveloppante (12) cylindrique circulaire. Selon l'invention, la zone d'appui (10) comprend également au moins un évidement radial (18) par rapport à l'axe de rotation (A) et à la surface enveloppante (12). L'invention concerne également un procédé de fabrication d'un arbre de ce type, procédé selon lequel au moins une partie de l'arbre est fabriquée au moyen d'un procédé de formage.
PCT/EP2009/000643 2008-02-07 2009-01-31 Arbre et procédé de fabrication d'un arbre, en particulier pour un moteur de véhicule automobile Ceased WO2009098005A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008008000A DE102008008000A1 (de) 2008-02-07 2008-02-07 Welle und Verfahren zum Herstellen einer Welle, insbesondere für einen Motor eines Kraftfahrzeugs
DE102008008000.4 2008-02-07

Publications (3)

Publication Number Publication Date
WO2009098005A2 true WO2009098005A2 (fr) 2009-08-13
WO2009098005A3 WO2009098005A3 (fr) 2009-12-03
WO2009098005A8 WO2009098005A8 (fr) 2013-06-20

Family

ID=40802035

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/000643 Ceased WO2009098005A2 (fr) 2008-02-07 2009-01-31 Arbre et procédé de fabrication d'un arbre, en particulier pour un moteur de véhicule automobile

Country Status (2)

Country Link
DE (1) DE102008008000A1 (fr)
WO (1) WO2009098005A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2600032A3 (fr) * 2011-12-01 2014-02-19 MAHLE International GmbH Arbre d'équilibrage

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009036067A1 (de) * 2009-08-04 2011-02-10 Schaeffler Technologies Gmbh & Co. Kg Verfahren zur Herstellung einer Ausgleichswelle
DE102010046163A1 (de) * 2010-09-21 2012-03-22 Magna Powertrain Ag & Co. Kg Massenausgleichseinheit
DE102017112895B4 (de) * 2017-06-12 2022-09-29 Hirschvogel Umformtechnik Gmbh Ausgleichswelle und Ausgleichswellenbaugruppe

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4237521A1 (de) * 1992-11-06 1994-05-11 Audi Ag Verfahren zum Herstellen einer gebauten Kurbelwelle für Hubkolbenmaschinen und verfahrensgemäße Kurbelwelle
DE19802484C2 (de) * 1998-01-23 2000-06-08 Daimler Chrysler Ag Verfahren und Vorrichtung zur Herstellung von gebauten Nockenwellen
JP2004100812A (ja) * 2002-09-09 2004-04-02 Hitachi Constr Mach Co Ltd 軸受装置
DE102007027990A1 (de) * 2007-06-14 2008-12-18 Herzog Intertec Gmbh Ausgleichswelle
DE202007011678U1 (de) * 2007-08-21 2007-10-18 Schaeffler Kg Ausgleichswelle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2600032A3 (fr) * 2011-12-01 2014-02-19 MAHLE International GmbH Arbre d'équilibrage
US8939124B2 (en) 2011-12-01 2015-01-27 Mahle International Gmbh Balancing shaft with bearing point having separated first and second bearing surfaces

Also Published As

Publication number Publication date
DE102008008000A1 (de) 2009-08-13
WO2009098005A8 (fr) 2013-06-20
WO2009098005A3 (fr) 2009-12-03

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