WO2016042055A1 - Système de paliers de support d'un arbre - Google Patents

Système de paliers de support d'un arbre Download PDF

Info

Publication number
WO2016042055A1
WO2016042055A1 PCT/EP2015/071280 EP2015071280W WO2016042055A1 WO 2016042055 A1 WO2016042055 A1 WO 2016042055A1 EP 2015071280 W EP2015071280 W EP 2015071280W WO 2016042055 A1 WO2016042055 A1 WO 2016042055A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
annular element
arrangement according
profiling
bearing arrangement
Prior art date
Application number
PCT/EP2015/071280
Other languages
German (de)
English (en)
Inventor
Holger Fröhlich
Original Assignee
Continental Automotive Gmbh
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 Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Publication of WO2016042055A1 publication Critical patent/WO2016042055A1/fr

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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller bearings

Definitions

  • the present invention relates to a bearing arrangement in a housing for supporting a shaft in a first bearing with a first bearing and in a second spaced from the first bearing second bearing with a second bearing.
  • Bearing arrangements with two bearings are used in a variety of ways in the art.
  • a bearing assembly is known to be used in the bushes of elastic materials. This arrangement allows protection against a current passage and allows vibration damping in the radial direction.
  • the disadvantage of this is that the adjustment of the axial preload, taking into account the spring travel for tolerance compensation of the bearing on the floating bearing side only on the modulus of elasticity of the sleeve made of elastic material is possible. If one additionally takes into account the thermal load on the non-locating bearing, only very limited possibilities of this bearing arrangement result due to the choice of material.
  • the present invention is therefore an object of the invention to provide a bearing assembly which overcomes the above drawback, so with the reliable so that a required axial pre ⁇ voltage is achieved to z. B. ensure a slip-free operation and thus an increase in the bearing life.
  • This object is achieved by a bearing ⁇ arrangement according to claim 1.
  • an inner sleeve enclosing and connected to the inner sleeve annular member is provided made of an elastic material.
  • the annular element has a profiling on at least one outer surface and / or in its interior.
  • the annular element is provided on at least two opposite outer sides with the profiling in order to achieve an efficient adjustment of the desired properties.
  • the elastic material of the annular element has the profiling in its internal structure.
  • changes in the ratio of loaded to unloaded surface can be made both on an outer periphery and in the interior of the annular element for profiling.
  • the annular element may be made of an elastomer, that is dimensionally stable, but elastically deformable and yet be resistant in these properties over a wide temperature range.
  • the annular member made of rubber, so vulcanized rubber or a polyurethane foam is formed.
  • the use of a polyurethane foam is low due to excellent elasticity, oil and old weathering resistance ⁇ .
  • the Shore hardness of the rubber materials used can be between 30 ° and 90 °.
  • the profiling is by at least one
  • At least one hollow chamber arranged in the interior of the annular element may form part of the profiling or the entire profiling.
  • the profiling can be varied in order to achieve the desired mechanical properties of the annular element. It can also be provided to use a plurality of juxtaposed and spaced-apart rings as an annular element.
  • the annular element may alternatively or additionally be enclosed by an outer sleeve.
  • the annular element and the outer sleeve are arranged radially one above the other on the inner sleeve.
  • the inner sleeve and the annular element are positively and / or cohesively ver ⁇ bound together to ensure safe operation of the bearing assembly to lienrangn. It can be provided that the inner sleeve and the annular element are connected to each other by gluing or by vulcanization. If the outer sleeve is used, this is typically likewise connected in a form-fitting and / or materially connected manner to the annular element. This can also be done by gluing or by vulcanization.
  • a coefficient of thermal expansion of a material of the outer sleeve is a maximum of 5 percent greater or smaller than a thermal expansion coefficient of the material of the housing to choose. This allows an adaptation of the two sleeves to the material contacting them in the bearing arrangement. If the thermal expansion coefficient of the bearing seat in the housing is too great, it may cause the outer sleeve in the housing seat to wander, which can lead to misalignment and tilting and thus increase wear.
  • the floating bearing is biased in the bearing assembly.
  • the axial preload should be one to two percent of the dynamic bearing yield.
  • the preload should be increased to three to four percent of the dynamic bearing yield.
  • An electric machine typically with a rotor and a stator, may comprise the described bearing arrangement. It may be provided here that the rotor has a rotor shaft which is mounted in rotor bearings.
  • the electric machine is typically used as a hybrid drive device in a motor vehicle.
  • FIG. 1 shows a rotor bearing of electrical machines in a side sectional view
  • Fig. 2 is an enlarged view of that shown in Fig. 1
  • Fig. 3 is a Fig. 2 corresponding view of another
  • Fig. 4 is a side view of a floating bearing bush with
  • FIG. 5 is a view similar to FIG. 4 of a loose bearing bush with a plurality of recesses on top and bottom of an annular element;
  • FIG. 5 is a view similar to FIG. 4 of a loose bearing bush with a plurality of recesses on top and bottom of an annular element;
  • Fig. 6 is a view similar to Figure 4 of a floating bearing bush with a plurality of recesses on the underside of an annular element.
  • Figure 7 is a side view of a built-floating bearing bush with zig-zag profiled annular element.
  • Fig. 8 is a view corresponding to Figure 7 with a ring-shaped member of polyurethane ⁇ .
  • Fig. 9 is a Fig. 7 corresponding view with a ring ⁇ shaped element in I-profile and
  • FIG. 1 An embodiment of a rotor bearing according to the invention is shown in Figure 1 in a side sectional view.
  • a fixed bearing 2 is arranged and axially spaced from the fixed bearing 2 a loose bearing 3 provided in a bearing plate 5.
  • a shaft 4 is mounted in the housing 1.
  • the fixed bearing 2 and the movable bearing 3 are designed as rolling bearings or deep groove ball bearings.
  • the floating bearing 3 is also axially biased to ensure a sufficient minimum load or bias in the axial direction under all operating conditions. For this purpose, the floating bearing 3 is in contact with the bearing plate via a floating bearing bush 10.
  • a structure of the floating bearing bush 10 is shown enlarged in Figure 2. Recurring features are provided with identical reference numerals in this as well as in the following figures.
  • the floating bearing 3 is arranged on the shaft 4 and via the Los ⁇ bearing bush 10, an inner sleeve 13, a form-fitting and cohesively inner sleeve 13 enclosing annular member 14 and the annular member 14 enclosing the outer sleeve 15, with the bearing plate 5 in contact ,
  • the axial bias which corresponds to about two percent of a dynamic bearing yield of the floating bearing.
  • the reference numeral 11 symbolizes a tolerance compensation for thermal expansion.
  • the reference numeral 12 symbolizes a vibration damping.
  • the annular element 14 is in the illustrated embodiment ⁇ example of rubber.
  • the inner sleeve 13 and the outer sleeve 15 are made of a metal, in the present embodiment of steel. On the outer sleeve 15 can be omitted in further embodiments.
  • the inner sleeve 13 is the same as the Au ⁇ .hülse 15 connected positively and cohesively by vulcanization to the annular member 14, but may also be bonded in other embodiments.
  • the annular element 14 has four recesses 16 on an upper side and a lower side facing each other. The recesses 16 are arranged tilted relative to a central axis of the movable bearing 10. Another embodiment of the movable bearing 10 is shown in Figure 3 in a figure 2 corresponding view. In contrast to the embodiment shown in Figure 2, the top and bottom of the annular member 14 are now closed, but four equally sized cavities 17 are provided in the interior of the annular member 14.
  • FIGS. 4 to 6 show a few basic examples for the design of a loose bearing bush.
  • Figure 4 shows a side sectional view of the floating bearing bush 10 with the annular member 14 and cavities 17 in the rubber.
  • the floating bearing bush 10 is shown with attached on the top and bottom recesses 16 as another embodiment.
  • FIG. 6 in further exemplary embodiments it is also possible to provide the recesses 16 only on one side, in the example shown only on the underside facing the inner sleeve 13.
  • the annular element 14 is profiled in a zigzag shape, that is to say that triangular recesses are arranged offset relative to one another on the upper side and the lower side.
  • the annular element 14 is made of polyurethane.
  • a polyurethane body with recesses or cavities may be used.
  • the annular element 14 is seated with the inner sleeve 13 on the bearing, however, in contrast to the example shown in Figure 7, the outer sleeve 15 is provided and in direct contact with the housing 1.
  • the loaded surfaces are in both embodiments shown on the top and bottom, while the sides represent unloaded surfaces 8.
  • the annular element 14 can also have a parallelogram-like profile shown in FIG. 10 c) or can be trapezoidal, as shown in FIG. 10 d) ,
  • the loaded surfaces 7 are located on the upper side and the lower side, while the sides represent unloaded surfaces 8.
  • FIG. 10b the sum of the loaded surfaces is reduced in FIG. 10d) and the sum of the unloaded surfaces is increased.
  • a T-shaped profile shown in FIG. 10 e) or an I-profile (FIG. 10 f)) also has symmetrical recesses on each side, which is not in contact with the outer sleeve 15 and / or the inner sleeve 13 Question.
  • the loaded surfaces 7 are again given by the top and bottom, while on the sides only unloaded surfaces 8 are present. By profiling these unloaded surfaces 8 are enlarged compared to a pure rectangular profile.
  • an H-profile as shown in Figure 10 g), in which a recess is disposed both on the top and the bottom, or the U-profile shown in Figure 10 h) with a recess only on the top can be used.
  • the described bearing arrangement is used for example in a hybrid drive of a passenger vehicle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)

Abstract

La présente invention concerne un système de paliers servant à supporter un arbre (4) dans un carter en un premier point d'appui comportant un premier palier (2) ou palier fixe, et en un second point d'appui écarté axialement du premier point d'appui et comportant un second palier (3) ou palier libre. Le second palier (3) ou palier libre est inséré dans un coussinet de palier libre (10) qui est formé par une douille intérieure (13) agencée sur le second palier (3) et par un élément annulaire (14) composé d'un matériau élastique, entourant la douille intérieure (13), et relié à cette dernière. L'élément annulaire (14) présente un profilage au moins sur une surface extérieure et/ou à l'intérieur.
PCT/EP2015/071280 2014-09-18 2015-09-17 Système de paliers de support d'un arbre WO2016042055A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014218808.3A DE102014218808A1 (de) 2014-09-18 2014-09-18 Lageranordnung zur Lagerung einer Welle
DE102014218808.3 2014-09-18

Publications (1)

Publication Number Publication Date
WO2016042055A1 true WO2016042055A1 (fr) 2016-03-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/071280 WO2016042055A1 (fr) 2014-09-18 2015-09-17 Système de paliers de support d'un arbre

Country Status (2)

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DE (1) DE102014218808A1 (fr)
WO (1) WO2016042055A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220364561A1 (en) * 2019-12-18 2022-11-17 Atlas Copco Airpower, Naamloze Vennootschap Compressor device and device equipped with a bearing damper

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017218481A1 (de) * 2017-10-16 2019-04-18 Bayerische Motoren Werke Aktiengesellschaft Lageranordnung

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001315653A (ja) * 2000-05-10 2001-11-13 Koyo Seiko Co Ltd 電動式舵取装置
US20010040067A1 (en) * 2000-05-10 2001-11-15 Koyo Seiko Co., Ltd. Electric power steering apparatus
JP2001322554A (ja) * 2000-05-17 2001-11-20 Koyo Seiko Co Ltd 電動式舵取装置
JP2002096749A (ja) * 2000-07-19 2002-04-02 Koyo Seiko Co Ltd 電動式舵取装置
US20020081050A1 (en) * 2000-12-06 2002-06-27 Herbert Cermak Shaft bearing assembly
DE102004006490B3 (de) * 2004-02-10 2005-04-21 Süddeutsche Gelenkscheibenfabrik GmbH & Co. KG Stützanordnung zur axial und radial nachgiebigen Abstützung eines Wellenlagers
EP1637769A1 (fr) * 2003-06-25 2006-03-22 NSK Ltd. Reducteur de vitesse de vis sans fin et systeme de direction a assistance electrique
DE102008014666A1 (de) * 2008-03-18 2009-09-24 SGF SüDDEUTSCHE GELENKSCHEIBENFABRIK GMBH & CO. KG Stützanordnung zur axial und radial nachgiebigen Abstützung eines Wellenlagers
DE102013109583A1 (de) * 2012-12-31 2014-07-03 Hyundai Motor Company Zentrallager-Buchseneinheit für eine Antriebswelle

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011012456A1 (fr) 2009-07-30 2011-02-03 Aktiebolaget Skf Agencement de paliers fixe et libre

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001315653A (ja) * 2000-05-10 2001-11-13 Koyo Seiko Co Ltd 電動式舵取装置
US20010040067A1 (en) * 2000-05-10 2001-11-15 Koyo Seiko Co., Ltd. Electric power steering apparatus
JP2001322554A (ja) * 2000-05-17 2001-11-20 Koyo Seiko Co Ltd 電動式舵取装置
JP2002096749A (ja) * 2000-07-19 2002-04-02 Koyo Seiko Co Ltd 電動式舵取装置
US20020081050A1 (en) * 2000-12-06 2002-06-27 Herbert Cermak Shaft bearing assembly
EP1637769A1 (fr) * 2003-06-25 2006-03-22 NSK Ltd. Reducteur de vitesse de vis sans fin et systeme de direction a assistance electrique
DE102004006490B3 (de) * 2004-02-10 2005-04-21 Süddeutsche Gelenkscheibenfabrik GmbH & Co. KG Stützanordnung zur axial und radial nachgiebigen Abstützung eines Wellenlagers
DE102008014666A1 (de) * 2008-03-18 2009-09-24 SGF SüDDEUTSCHE GELENKSCHEIBENFABRIK GMBH & CO. KG Stützanordnung zur axial und radial nachgiebigen Abstützung eines Wellenlagers
DE102013109583A1 (de) * 2012-12-31 2014-07-03 Hyundai Motor Company Zentrallager-Buchseneinheit für eine Antriebswelle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220364561A1 (en) * 2019-12-18 2022-11-17 Atlas Copco Airpower, Naamloze Vennootschap Compressor device and device equipped with a bearing damper
US12012960B2 (en) * 2019-12-18 2024-06-18 Atlas Copco Airpower Naamloze Vennootschap Compressor device and device equipped with a bearing damper

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Publication number Publication date
DE102014218808A1 (de) 2016-03-24

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