WO2004091995A2 - Palier a friction a absence de jeu - Google Patents

Palier a friction a absence de jeu Download PDF

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Publication number
WO2004091995A2
WO2004091995A2 PCT/US2004/010839 US2004010839W WO2004091995A2 WO 2004091995 A2 WO2004091995 A2 WO 2004091995A2 US 2004010839 W US2004010839 W US 2004010839W WO 2004091995 A2 WO2004091995 A2 WO 2004091995A2
Authority
WO
WIPO (PCT)
Prior art keywords
friction
bushing
load assembly
friction ring
ring
Prior art date
Application number
PCT/US2004/010839
Other languages
English (en)
Other versions
WO2004091995A3 (fr
Inventor
Ryan C. Noss
Michael D. Beaman
Original Assignee
Timken U.S. Coporation
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 U.S. Coporation filed Critical Timken U.S. Coporation
Publication of WO2004091995A2 publication Critical patent/WO2004091995A2/fr
Publication of WO2004091995A3 publication Critical patent/WO2004091995A3/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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/02—Vibration-dampers; Shock-absorbers with relatively-rotatable friction surfaces that are pressed together
    • F16F7/06—Vibration-dampers; Shock-absorbers with relatively-rotatable friction surfaces that are pressed together in a direction perpendicular or inclined to the axis of rotation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/16—Steering columns
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/001—Mechanical components or aspects of steer-by-wire systems, not otherwise provided for in this maingroup
    • B62D5/005—Mechanical components or aspects of steer-by-wire systems, not otherwise provided for in this maingroup means for generating torque on steering wheel or input member, e.g. feedback

Definitions

  • This invention relates generally to bearing assemblies having a flexible annular bushing and, more particularly, to a bearing assembly suitable for the mounting of steering columns and similar applications.
  • a bearing assembly is required that isolates a shaft, for example a steering column, with respect to noise and vibration, hi addition, a "zero clearance" bearing may be desired in those applications to further improve noise and vibration characteristics and maintain a "tight" feel.
  • a driver is accustomed to a tactile feel of a relatively smooth rotation that requires some effort to rotate the steering wheel to avoid over steering or a loose feel.
  • a component is typically provided about the steering shaft to cause a friction load on the shaft with a resultant "torque-to-rotate" value within a range that provides the desired tactile feel.
  • FIG. 1 One example of a friction loading device 10 is shown in Fig. 1.
  • the device 10 provides a plurality of fingers 12 positioned about the shaft 20.
  • a spring 14 is placed about the fingers 12 to urge the fingers 12 in to engagement with the shaft 20 to cause a desired friction load thereon.
  • Such a device 10 has been found to be difficult to assemble and to cause other undesirable effects, for example, unwanted noise.
  • the present invention provides a friction load assembly for positioning about a shaft.
  • the friction load assembly includes an elastomeric bushing formed about a friction ring.
  • the friction ring includes a body that defines an internal bearing surface. The diameter of the internal bearing surface is slightly smaller than the external diameter of the shaft.
  • the friction ring preferably has a split body such that it can expand against the elastomeric bushing as the load assembly is positioned about the shaft. The materials and configurations of the bushing and split ring allow the amount of frictional load applied to the shaft to be defined.
  • the friction load assembly may also be formed with a load bearing rolling assembly incorporated therein.
  • the rolling assembly is configured to bear against the shaft while the friction ring provides a friction load thereto.
  • Fig. 1 is an isometric view of a prior art friction loading device positioned about a shaft.
  • Fig. 2 is a side elevation view of a bearing assembly that is a first embodiment of the present invention.
  • Fig. 3 is a section view of the bearing assembly of Fig. 2, taken along the line 3-3 in Fig. 2, positioned adjacent a shaft.
  • Fig. 4 is an isometric view of the split friction ring of the bearing assembly of Fig. 2.
  • Fig. 5 is a side elevation view of an assembled bushing and split friction ring of the bearing assembly of Fig. 2.
  • Fig. 6 is a partial section view of a bearing assembly that is a second embodiment of the present invention.
  • Fig. 7 is a partial section view of a bearing assembly that is a third embodiment of the present invention.
  • the bearing assembly 50 generally comprises a retaining cup 52 positioned about a bushing 70 and a friction ring 60.
  • the cup 52 preferably has opposed lips 54 and 56 extending inward to retain the friction ring 60 and bushing 70.
  • the cup 52 is preferably a drawn cup formed of soft steel with the lips 54, 56 curled radially inwardly to provide the required axial retention.
  • Other retention structures for example, a sleeve, may also be utilized.
  • a cup or other retention structure does not have to be provided. As can be seen in Fig.
  • the friction ring 60 is retained such that it has an internal diameter D that is slightly smaller than the intended shaft diameter S. As such, the friction ring 60 contacts the shaft 20 and causes a friction load which must be overcome to rotate the bearing assembly 50 about the shaft 20. As will be described hereinafter, the characteristics of the bearing assembly 50 can be adjusted to achieve a "torque-to-rotate" value.
  • the friction ring 60 has a cylindrical body 62 which defines an internal bearing surface 64.
  • the bearing surface 64 may extend across the entire body 62, but preferably includes outward tapers 66 that assist in sliding the bearing assembly 50 on to the shaft 20.
  • the outer surface of the body 62 preferably has inward tapers 67 that assist formation of the bushing 70 about the friction ring 60, as shown in Figs. 3 and 5.
  • the friction ring 60 preferably has a split 68 extending across the body 62. The split 68 allows the internal diameter D of the friction ring 60 to be varied.
  • the bushing 70 can be molded about the friction ring 60 to reduce the spacing of the split 68 to achieve a desired internal diameter D. Additionally, the split 68 allows the friction ring 60 to expand slightly against the elastomeric bushing 70 as the bearing assembly 50 is positioned on a shaft 20. The split 68 provides greater ability to control the interference between the friction ring 60 and the shaft 20 to better control the friction load on the shaft 20.
  • the friction ring 60 is preferably manufactured from a thermoplastic material, but various materials may be utilized. Materials having different coefficients of friction may be utilized to achieve different frictional loads on the shaft 20. Additionally, while the bearing surface 64 is shown as a planar surface, it may have other configurations. For example, the bearing surface 64 may be provided with recesses or the like to vary the frictional contact or to promote fluid flow through if such is desired in a particular application. Additionally, the width of the bearing surface 64 may be adjusted to provide various interference.
  • the bushing 70 is manufactured about the friction ring 60, preferably by molding, to achieve the preloaded friction assembly 80 illustrated in Fig. 5.
  • This friction assembly 80 may be positioned in a cup 52, as shown in Figs. 2 and 3, or the like, or it may be used independently.
  • the friction assembly 80 may be positioned about a shaft 20 and supported in a housing or the like without any cup.
  • the bushing 70 is preferably manufactured from an elastomeric material which may be a natural or synthetic material.
  • the bushing 70 may be formed from a natural rubber or molded of an engineered thermoplastic elastomer, for example Sarlmk, available from DSM Themoplastic Elastomers Incorporated.
  • the bushing 70 may be provided with a contoured outer surface 72 to facilitate engagement of the bushing 70 with the intended cup 52 or an intended housing or the like.
  • the rolling assembly 180 preferably includes a cage 182 supporting a plurality of rolling elements 184.
  • the rolling elements 184 are can be needle rollers, balls or the like. Additionally, the cage 182 may be eliminated.
  • An external race 186 is provided about the rolling elements 184 and is supported by the bushing 170. The bushing 170 urges the race 186, and thereby the rolling elements 184, inward to define a zero clearance bearing about the shaft 20.
  • Each bearing assembly 150, 250 preferably includes a cup 152 positioned about the bushing 170 and the rolling assembly 180 to retain the bearing assembly 150, 250 together.
  • Bearing assembly 150 includes a single friction ring 160 positioned within the bearing assembly 150 to provide a desired friction load against the shaft 20.
  • the friction ring 160 is positioned adjacent to the rolling assembly 180 and is enclosed by the bushing 170 similar to the previous embodiment.
  • the friction ring 160 may be narrowed to facilitate the rolling assembly 180.
  • the friction ring 160 has an internal bearing surface 164 that extends slightly inward of the rolling elements 184.
  • the friction ring 160 when the bearing assembly 150 is positioned on the shaft 20, the friction ring 160 will expand slightly against the bushing 170 and will have a diameter equal to the shaft 20, which is also preferably the internal diameter of the rolling assembly 180, while applying a friction load against the shaft 20.
  • the load can be adjusted in the manner described above with respect to the first embodiment.
  • Bearing assembly 250 is similar to the previous embodiment, but includes a friction ring 160 positioned on each side of the rolling assembly 180. The position, size and configuration of each friction ring 160 can be adjusted to provide desired friction loads.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Support Of The Bearing (AREA)

Abstract

Ensemble charge de friction (50) destiné à être placé autour d'un arbre (20), qui comporte une bague élastomère (70) formée autour d'un anneau de friction (6). L'anneau de friction comporte un corps définissant une surface de palier interne (64), le diamètre de la surface de palier interne étant légèrement inférieur au diamètre externe de l'arbre (5). L'anneau de friction peut comporter un corps fendu de manière à pouvoir s'étendre contre la bague élastomère lorsque l'ensemble charge est placé autour de l'arbre. Les matériaux et les configurations de la bague et de l'anneau fendu permettent de définir la charge de friction appliquée à l'arbre. Un ensemble palier à roulement peut également être incorporé dans l'ensemble charge de friction.
PCT/US2004/010839 2003-04-08 2004-04-08 Palier a friction a absence de jeu WO2004091995A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US46122703P 2003-04-08 2003-04-08
US60/461,227 2003-04-08

Publications (2)

Publication Number Publication Date
WO2004091995A2 true WO2004091995A2 (fr) 2004-10-28
WO2004091995A3 WO2004091995A3 (fr) 2005-01-20

Family

ID=33299785

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2004/010839 WO2004091995A2 (fr) 2003-04-08 2004-04-08 Palier a friction a absence de jeu

Country Status (1)

Country Link
WO (1) WO2004091995A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1655202A2 (fr) * 2004-11-04 2006-05-10 TRW Automotive GmbH Ensemble avec volant et un générateur de résistance de la direction
WO2011161492A1 (fr) * 2010-06-23 2011-12-29 Aktiebolaget Skf Dispositif de friction pour un ensemble palier, palier et ensemble palier comportant un tel dispositif de friction
WO2012084016A1 (fr) * 2010-12-21 2012-06-28 3E Couronne d'orientation coulissante dotée d'une rigidité rotative dépendant de la charge du rotor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB481974A (en) * 1936-10-06 1938-03-22 Frank Sidebotham Rippingille Improvements relating to oscillatory or pivotal joints
GB805538A (en) * 1955-02-01 1958-12-10 Wright Howard Clayton Ltd Improvements relating to steering columns for motor vehicles
FR2537226A1 (fr) * 1982-12-03 1984-06-08 Sagem Palier a glissement
US4854141A (en) * 1985-05-31 1989-08-08 Nacam Anti-rotation locking device including a torque limitation for a motor vehicle steering column

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB481974A (en) * 1936-10-06 1938-03-22 Frank Sidebotham Rippingille Improvements relating to oscillatory or pivotal joints
GB805538A (en) * 1955-02-01 1958-12-10 Wright Howard Clayton Ltd Improvements relating to steering columns for motor vehicles
FR2537226A1 (fr) * 1982-12-03 1984-06-08 Sagem Palier a glissement
US4854141A (en) * 1985-05-31 1989-08-08 Nacam Anti-rotation locking device including a torque limitation for a motor vehicle steering column

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1655202A2 (fr) * 2004-11-04 2006-05-10 TRW Automotive GmbH Ensemble avec volant et un générateur de résistance de la direction
EP1655202A3 (fr) * 2004-11-04 2006-09-06 TRW Automotive GmbH Ensemble avec volant et un générateur de résistance de la direction
WO2011161492A1 (fr) * 2010-06-23 2011-12-29 Aktiebolaget Skf Dispositif de friction pour un ensemble palier, palier et ensemble palier comportant un tel dispositif de friction
CN103080580A (zh) * 2010-06-23 2013-05-01 Skf公司 用于轴承组件的摩擦装置，包括该摩擦装置的轴承组件和轴承
US8950946B2 (en) 2010-06-23 2015-02-10 Aktiebolaget Skf Friction device for a bearing assembly, bearing and bearing assembly comprising such a friction device
CN103080580B (zh) * 2010-06-23 2016-03-16 Skf公司 用于轴承组件的摩擦装置，包括该摩擦装置的轴承组件和轴承
WO2012084016A1 (fr) * 2010-12-21 2012-06-28 3E Couronne d'orientation coulissante dotée d'une rigidité rotative dépendant de la charge du rotor

Also Published As

Publication number Publication date
WO2004091995A3 (fr) 2005-01-20

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