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WO2011002740A1 - Procédé et appareil permettant d'assurer l'étanchéité de surfaces de faces arrière de bagues de roulement exposées - Google Patents

Procédé et appareil permettant d'assurer l'étanchéité de surfaces de faces arrière de bagues de roulement exposées Download PDF

Info

Publication number
WO2011002740A1
WO2011002740A1 PCT/US2010/040323 US2010040323W WO2011002740A1 WO 2011002740 A1 WO2011002740 A1 WO 2011002740A1 US 2010040323 W US2010040323 W US 2010040323W WO 2011002740 A1 WO2011002740 A1 WO 2011002740A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
inner race
shield
backface
bearing
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/US2010/040323
Other languages
English (en)
Inventor
Michael A. Gromosiak
Matthew B. Turi
Steven A. Kuhn
Frederic C. Billet
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.)
Timken Co
Original Assignee
Timken Co
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 Timken Co filed Critical Timken Co
Publication of WO2011002740A1 publication Critical patent/WO2011002740A1/fr
Anticipated expiration legal-status Critical
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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the present invention relates generally to an apparatus and method for preventing contaminates from entering a bearing assembly, such as a vehicle wheel hub assembly, and in particular to a seal for protecting exposed race backface surfaces and for excluding contaminates from the interior of the bearing assembly.
  • bearing assemblies for supporting a rotating member axially relative to a fixed or stationary member are known. Rolling elements in these bearing assemblies are disposed between inner and outer races fitted to the fixed or stationary members being supported, and provide rolling support between the two members.
  • One common application for bearing assemblies is in mounting the road wheels of automotive vehicles on the suspension systems of such vehicles.
  • One such arrangement relies on a dead spindle which projects from the suspension system - usually from a steering knuckle - into a hub to which a road wheel is bolted.
  • the hub rotates around the spindle on antifriction bearings that are located between the hub and the spindle.
  • the hub to which the road wheel is bolted has a live spindle which projects into a housing which in turn is bolted to a steering knuckle or other suspension system component.
  • An antifriction bearing located between the spindle and housing enables the spindle - and indeed the entire hub - to rotate relative to the housing.
  • the bearings that are located around the spindle must have barriers of one type or another to exclude external contaminants from entering into them.
  • a dead spindle typically a seal is fitted to the inboard end of the hub, to wipe against a wear surface on the spindle. An end cap is then pressed into the outboard end of the hub, enclosing the seal and spindle end.
  • a live spindle such as used for a non-driven wheel, the outboard end of the bearing contains a live seal.
  • the inboard end of the bearing may be fitted with a live seal or the inboard end of the housing or the steering knuckle itself may be fitted with a cover that isolates inboard end of the bearing, but this increases the expense of hub assembly.
  • the live spindle is coupled to a drive shaft through a constant velocity (CV) joint, both the inboard and outboard ends of the bearing require live seals.
  • CV constant velocity
  • the inboard side of a vehicle wheel hub assembly and bearing i.e., the side facing the center of the vehicle, is commonly exposed to a significant amount of environmental contamination in automotive applications.
  • Environmental contamination may impact sealing performance and accelerate corrosion on exposed ferrous surfaces of the wheel hub assembly, such as the inboard inner race backface surfaces, i.e. those surfaces of the inboard inner race which are exposed to the inboard end of the bearing.
  • Corrosion on the inboard inner race backface surfaces and hoop stress levels present within the inner race structures have been linked to inner race corrosion cracking.
  • the present disclosure provides a bearing assembly with an elastomeric seal and shield which provides the dual purpose sealing properties of: (1) reducing seal contaminate ingress between the inner diameter of a bearing seal and the inner race large rib outer diameter surface facing the bearing seal; and (2) providing protection against inner race hoop-stress corrosion cracking due to contaminate pitting and corrosion on exposed inner race component surfaces.
  • the elastomeric seal and shield includes sleeve portion and an annular flange portion arranged with a generally L-shaped cross-section. The sleeve portion is adapted to seat against the inner race outer diameter surface, between the inner race outer diameter and an inner diameter of the adjacent bearing seal shield carried by an outer race or associated structure.
  • the integrated annular flange portion projects radially inward from the sleeve portion, covering the exposed portion of the inner race backface surface, and is partially entrapped between a bearing attachment means such as a shoulder, formed end, or threaded member and the inner race backface surface.
  • the present disclosure provides a vehicle wheel hub and bearing assembly with an inboard elastomeric seal and shield which provides the dual purpose sealing properties of: (1) reducing inboard seal contaminate ingress between the inner diameter of the bearing seal shield and the inboard inner race and seal engagement surface; and (2) providing protection against inboard inner race hoop-stress corrosion cracking due to contaminate pitting and corrosion on the inboard inner race backface surface, and backface outer diameter radius.
  • the shield includes a sleeve portion and annular flange portion in an L-shaped configuration, and may be a separate component or integrated with the elastomeric seal.
  • the sleeve portion is adapted to seat against the inboard inner race outer diameter surface, between the inner race seal engagement surface and an inner diameter of the adjacent bearing seal shield.
  • the integrated annular flange portion projects radially inward from the inboard end of the sleeve portion, covering the exposed portion of the inboard inner race backface surface, and is entrapped within the outer diameter of a roll form or threaded member and the inner race backface surface.
  • the elastomeric seal and shield is defined by an annular ring of elastomeric material which is disposed to seat with an interference fit within an annular recess at the intersection of an inboard inner race backface surface and inner seal engagement surface, between a package bearing seal shield inner diameter and the inboard inner race seal engagement surface.
  • Figure 1A is a partial sectional view of a wheel assembly illustrating placement of the L-shaped bearing shield of the present disclosure
  • Figure 1 B is an enlarged view of the placement of the L-shaped bearing shield in Fig. 1A, as indicated at section 1 B;
  • Figure 2 is a perspective view of the annular L-shaped bearing shield of the present disclosure
  • Figure 3 is a cross-sectional view of an L-shaped bearing shield of Fig 2;
  • Figure 4 is a perspective view of the annular L-shaped bearing shield of Fig. 2 installed on an inboard end of a bearing assembly;
  • Figure 5 is a sectional view of an alternate configuration for a bearing shield of the present disclosure.
  • an exemplary vehicle wheel hub and bearing assembly 10 is shown consisting of a rotating hub 12 onto which a vehicle wheel (not shown) is secured by multiple wheel lug bolts 14 on an outboard end.
  • a hub and bearing assembly 10 enables a vehicle wheel and brake disk (not shown) to rotate about an axis X-X on a steering knuckle or other component of an automotive suspension system (not shown).
  • the hub and bearing assembly 10 includes a spindle 16 to which the road wheel and brake disk are secured, a housing 18 which is mounted on the steering knuckle or other suspension component (not shown), and a bearing 20 which is located between the hub 16 and housing 18, and which enables the hub 16 to rotate relative to the housing 18 with minimum friction.
  • Optional sensors 17 for measuring speed and/or forces on the hub and bearing assembly 10 may be mounted to the housing 18.
  • the hub 16 includes a flange 22 and the spindle
  • the flange 22 which may be integral with the flange 22, and which projects from the flange 22 at a shoulder region 26 located on the back face 28 of the flange 22. Radially outward from the shoulder region, the flange 22 is fitted with the lug bolts 14 which project axially from its front face 30.
  • the brake disk (not shown) seats against the flange front face 30, and the road wheel (not shown) in turn seats against the brake disk with the lug bolts 14 projecting though both the brake disk and the wheel.
  • lug nuts are threaded over the exposed ends of the lug bolts 14 to secure the brake disk and wheel to the hub flange 22.
  • An attachment member 25 is disposed at an inboard end 25A, remote from the hub flange 22.
  • the attachment member 25 may be integrally formed where the spindle 24 is upset, that is, deformed radially outwardly in the provision of a roll-formed end having an abutment face 32 that lies perpendicular to the axis X-X and is presented toward the shoulder region 26.
  • the bearing 20 is captured between the shoulder region 26 on the flange 22 and the abutment face 32 of attachment member or formed inboard end 25 of the spindle 24.
  • the formed inboard end may be replaced by a threaded region on an outer diameter of the spindle 24, onto which a discrete attachment member such as a retaining nut (not shown) is threaded, capturing the bearing 20 between the abutted shoulder region 26 on the flange 22 and the threaded retaining nut.
  • a discrete attachment member such as a retaining nut (not shown) is threaded, capturing the bearing 20 between the abutted shoulder region 26 on the flange 22 and the threaded retaining nut.
  • the bearing 20 includes inboard inner race 34 and an outboard inner race 36 which fit around the outer diameter of the spindle 24, there being an interference fit between each of the inner races 34, 36 and the spindle 24.
  • the outboard inner race 36 may be integrally formed into the outer diameter surface of the spindle 24, adjacent the shoulder region 26.
  • Each inner race 34, 36 of the bearing 20 have a tapered raceway 34A, 36A, that is presented outwardly away from the axis X-X.
  • a thrust rib 34B, 36B is disposed at the large end of each tapered raceway 34A, 36A, and each discrete inner race 34, 36 includes a back face 34C, 36C which is squared off with respect to the axis X-X at an end of the associated thrust rib 34B, 36B.
  • the inboard inner race 34 abuts a small end of the outboard inner race 36 along the spindle 24, that is to say, the two inner races 34, 36 abut at their front faces 34D, 36D.
  • the back face 36C of the outboard inner race 36 may abut the shoulder region 26 that lies along the flange 22 or, as shown in Fig. 2A, may be integrally formed therein.
  • the bearing 20 includes rolling elements 38, such as tapered rollers, arranged in two rows, there being a separate row around each of the inner races 34, 36.
  • the rolling elements 38 extend around the raceways 34A, 36A for each of the inner races 34, 36, and for cylindrical or tapered rollers, there being essentially a line contact between the faces of the rolling elements 38 and raceways 34A, 36A.
  • the large-end faces of the rollers 38 are preferably disposed to bear against the thrust ribs 34B, 36B.
  • the tapered rollers 38 of each row shown in Fig. 1A are essentially on apex, which means that the envelopes in which their tapered side faces lie have their apices located at a common point.
  • Each row of rollers 38 has an associated cage 40 to maintain the proper spacing between the rollers 38 in that row.
  • the housing 18 surrounds the spindle 24 as well as the two inner races 34, 36 and the two rows of rollers 38.
  • the housing 18 forms part of the bearing 20, in that the housing includes raceways 42A, 44A which are presented inwardly toward the axis X-X. In that sense, the housing 18 provides the inboard and outboard outer races 42, 44 of the bearing 20.
  • the raceways 42A, 44A on the housing 18 taper downwardly toward an intervening surface 46 which separates them.
  • the rollers 38 likewise lie along the raceways 42A, 44A of the housing 18, essentially line contact between the raceways and the faces of the rollers 38.
  • each end of the bearing 20 has an annular space, with that space being between the thrust rib 34B, 36B at that end, and the surrounding surface which defines the end bores 48.
  • an embodiment of the present disclosure incorporates an inboard elastomeric seal and shield 100 which functions: (1) to reduce inboard seal contaminate ingress between the package bearing seal 50 inner diameter, defined by either the flexible seal element or a seal shield if present, and an inboard inner race seal engagement surface 52, associated with the rotating spindle 24; and (2) to provide protection against hoop stress corrosion cracking in the inboard inner race 34 due to contaminate pitting and corrosion on the surface of the inboard inner race backface 34C and backface outer diameter radius 34E.
  • the elastomeric seal and shield 100 includes sleeve portion 102 and an annular flange portion 104 arranged with a radially inwardly directed "L" shaped cross-section, shown in Figs. 1 B and 3.
  • the sleeve portion 102 is adapted to seat against the inboard inner race seal engagement surface 52, preferably with an interference fit, between the outer diameter of the inner race large rib 34B and an inner diameter of the adjacent package bearing seal 50.
  • the integrated annular flange portion 104 projects radially inward from the inboard end of the sleeve portion 102, covering the exposed surface portion of the inboard inner race backface 34C and backface OD radius (Fig.
  • the annular flange portion 104 against the inboard inner race backface 34C.
  • the outer diameter of the inboard end of the spindle 24 may have threads and a discrete attachment member such as a nut (not shown) may be engaged with those threads and turned down against the surface of the annular flange 104 to entrap it against the surface of the inner race backface 34C.
  • the elastomeric seal and shield 100 is defined by an annular ring 200 of a polymer or elastomeric material which is either disposed to seat with an interference fit, or which is molded directly to the inner race backface surface 34C.
  • the annular ring 200 is retained within an annular recess 54 at the intersection of a surface of an inboard inner race backface 34C and seal engagement surface 52, between the package bearing seal 50 inner diameter and the inboard inner race seal engagement surface 52.
  • Axial entrapment of the annular ring 200 by the attachment member 25 on the spindle member 24 which overlaps the inboard surface of the annular ring 200 serves to further secure the annular ring 200 in place.
  • the backface surface 34C and backface OD radius of the inboard inner race 34 is protected from direct exposure to environmental contaminates by the annular ring 200, while the molding or interference fit to the package bearing seal 50 inner diameter reduces contaminate ingress between the package bearing seal 50 and the inboard inner race seal engagement surface 52.
  • the specific material from which the elastomeric seal and shield 100 is formed need not be limited to an elastomeric material, and that a seal and shield 100 embodying the concepts and features of the present disclosure may be manufactured from any material suitable for the particular application in which it is to be utilized, without departing from the scope of the present disclosure.
  • Specific dimensions or sizes of the elements of the seal and shield 100 are not limited to any sizes or configurations shown herein or in the Figures.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un ensemble moyeu et palier (10) présentant un joint d'étanchéité et un flasque (100), comprenant une partie manchon (102) et une partie flasque annulaire (104) présentant une section transversale en forme de "L". La partie manchon (102) est conçue pour reposer contre une surface de contact d'étanchéité de bague de roulement intérieure (52), entre cette dernière et un diamètre intérieur du joint d'étanchéité de palier adjacent (50). La partie de flasque annulaire intégrée (104) fait saillie radialement vers l'intérieur depuis la partie manchon, recouvrant ainsi une partie exposée de la surface de face arrière de bague de roulement intérieure (34C) et du rayon du diamètre extérieur de la face arrière, et est piégée entre un élément de fixation (25) fixé à une broche soutenant la bague de roulement intérieure (34) et la surface de face arrière de bague de roulement intérieure (34C).
PCT/US2010/040323 2009-06-30 2010-06-29 Procédé et appareil permettant d'assurer l'étanchéité de surfaces de faces arrière de bagues de roulement exposées Ceased WO2011002740A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US22163509P 2009-06-30 2009-06-30
US61/221,635 2009-06-30

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US13/318,459 A-371-Of-International US9108713B2 (en) 2009-09-09 2010-09-09 Elevon control system
US14/796,906 Division US10696375B2 (en) 2009-09-09 2015-07-10 Elevon control system

Publications (1)

Publication Number Publication Date
WO2011002740A1 true WO2011002740A1 (fr) 2011-01-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2010/040323 Ceased WO2011002740A1 (fr) 2009-06-30 2010-06-29 Procédé et appareil permettant d'assurer l'étanchéité de surfaces de faces arrière de bagues de roulement exposées

Country Status (1)

Country Link
WO (1) WO2011002740A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112762099A (zh) * 2019-10-21 2021-05-07 通用汽车环球科技运作有限责任公司 模块化迷宫式轴承组件

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5022659A (en) 1988-12-27 1991-06-11 The Timken Company Seal assembly for antifriction bearings
US6561559B1 (en) * 1998-03-23 2003-05-13 Skf Engineering And Research Centre B.V. Bearing unit, in particular railway axlebox bearing unit, having improved anti-fretting behavior
US20040228556A1 (en) * 2003-04-17 2004-11-18 Hisashi Ohtsuki Bearing for a wheel of vehicle
JP2006200708A (ja) * 2005-01-24 2006-08-03 Ntn Corp 車輪用軸受
WO2008006339A1 (fr) * 2006-07-12 2008-01-17 Schaeffler Kg Système de palier d'un moyeu de roue d'un véhicule, pouvant être entraîné par un articulation tournante

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5022659A (en) 1988-12-27 1991-06-11 The Timken Company Seal assembly for antifriction bearings
US6561559B1 (en) * 1998-03-23 2003-05-13 Skf Engineering And Research Centre B.V. Bearing unit, in particular railway axlebox bearing unit, having improved anti-fretting behavior
US20040228556A1 (en) * 2003-04-17 2004-11-18 Hisashi Ohtsuki Bearing for a wheel of vehicle
JP2006200708A (ja) * 2005-01-24 2006-08-03 Ntn Corp 車輪用軸受
WO2008006339A1 (fr) * 2006-07-12 2008-01-17 Schaeffler Kg Système de palier d'un moyeu de roue d'un véhicule, pouvant être entraîné par un articulation tournante

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112762099A (zh) * 2019-10-21 2021-05-07 通用汽车环球科技运作有限责任公司 模块化迷宫式轴承组件

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