WO1999020912A1 - A plane bearing assembly - Google Patents
A plane bearing assembly Download PDFInfo
- Publication number
- WO1999020912A1 WO1999020912A1 PCT/US1998/022089 US9822089W WO9920912A1 WO 1999020912 A1 WO1999020912 A1 WO 1999020912A1 US 9822089 W US9822089 W US 9822089W WO 9920912 A1 WO9920912 A1 WO 9920912A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- end portions
- bearing assembly
- intermediate portion
- recited
- plane bearing
- Prior art date
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
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/20—Sliding surface consisting mainly of plastics
-
- 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
- F16C27/02—Sliding-contact bearings
-
- 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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/52—Polyphenylene sulphide [PPS]
-
- 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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/60—Polyamides [PA]
Definitions
- This disclosure relates to a plane bearing assembly.
- a bearing that provides a minimal amount of deformation to its inner working surface.
- Plane bearings define a lubricated surface to engage a translating or rotating shaft.
- Plane bearings are commonly used for such applications as automotive door-lift mechanisms, belt tensioners, seat height and position adjustment mechanisms, etc.
- This type of bearing is used to support rotating or reciprocating members or combinations of both motions.
- the object is to provide a bearing that incorporates the low friction, wear resistance, and lubricating properties into the bore of the bearing to allow efficient motion therein.
- Polymer type bearings are often used for their desired properties (see Thomson U.S. Patent No. 2,675,283).
- Rosen U.S. Patent No. 4,913,562 teaches a center flange arrangement wherein the flange engages the housing by an internal groove.
- the internal groove must be added to the housing often requiring added expense due to machining costs.
- the flange must be designed to properly fit within the bore and the groove engaging it. Further external flanges make it difficult to insert the bearing into the housing.
- 4,913,562 addresses this difficulty by creating a diagonal slit longitudinally down the bearing.
- the bearing can now be flexed helically to install it into the housing bore.
- the slit must be incorporated into the molding process of the bearing creating additional tooling expense.
- a bearing that can be molded using a simple technique, that is without slits or flanges. Further, it is desirable to provide a bearing that is easy to install, eliminating the need to create helical slits or cuts within the bearing. Additionally, a bearing that supports a shaft continuously without an interruption of a diagonal slit is preferred.
- a plane bearing assembly includes a bearing defining a longitudinal axis and having an intermediate portion bounded on opposed longitudinal ends by first and second end portions.
- the intermediate portion has an inner working surface and an outer relief surface.
- the first and second end portions have an outer surface which extends radially outward from the outer relief surface of the intermediate portion such that the intermediate portion can be relieved relative to the first and second end portions without substantial deformation of the inner working surface.
- FIG. 1 is an isometric view of a preferred embodiment of an improved bearing assembly
- FIG. 2 is a cross-sectional view of a preferred embodiment of an improved bearing assembly
- FIG. 3 shows a cross section of the bearing assembly installed within a housing bore with a shaft passing through the bearing; and FIG. 4 shows a magnified cross-sectional view of end portion 16.
- FIG. 5 shows a cross-sectional view of housing structure 26 wherein interior surface 34 includes different diameters.
- An improved bearing assembly is cylindrically shaped with raised end portions.
- the raised end portions create an interference fit with the interior of a housing bore in which it is installed.
- the improved bearing provides a low friction, low wear surface for contacting a shaft within its internal bore.
- the internal bore provides a working surface that is continuous for consistent contact with a shaft during operation. Further the press-fit of the bearing minimizes close- in over the working interior bore of the bearing, that is the bearing's inside diameter does not impinge significantly on the clearance between the bearing and the shaft.
- FIG. 1 is an isometric view of a preferred embodiment of a plane bearing 10.
- FIG. 2 is a cross-sectional view of a preferred embodiment of bearing 10.
- the bearing assembly defines a bore 11.
- Bearing 10 is generally cylindrical in shape with two end portions 14 and 16.
- the bearing has an intermediate portion 12 which has an inner working surface 18 which supports a shaft 28 during operation.
- End portions 14 and 16 maintain a constant wall thickness which is approximately equal to the wall thickness of the intermediate portion 12. However, other thicknesses for end portions 14 and 16 are contemplated. Outer surfaces 22 and 24 of the end portions 14 and 16 are extended radially outward beyond the intermediate portion's outer relief surface 20. Also, a preferred embodiment includes inner surfaces 30 and 32 of end portions 14 and 16 which define a larger diameter than inner working surface 18 of intermediate portion 12 of bearing 10. Because end portions 14 and 16 are raised, outer relief surface 20 is defined in intermediate portion 12 of bearing 10. Slots 23 may also be formed in end portions 14 and 16. These slots 23 facilitate accommodation of bearing 10 in a carriage.
- FIG. 3 shows a cross section of a bearing assembly 8 installed within a housing bore with a shaft passing through bearing 10.
- a housing structure 26 defines a bore having an interior surface 34.
- Bearing 10 is press-fit into housing structure 26.
- Outer surfaces 22 and 24 of end portions 14 and 16 contact interior surface 34 of housing structure 26.
- the diameter of housing structure 26 is less than the diameter defined by outer surfaces 22 and 24 of end portions 14 and 16. Therefore, an interference fit is created.
- Bearing 10 may be made of a compliant material which can deform at end portions 14 and 16 (See FIG. 4).
- outer relief surface 20 of intermediate portion 12 does not contact interior surface 34 of housing structure 26.
- Inner working surface 18 is in contact with shaft 28, however enough clearance is allocated for shaft 28 to translate, rotate or translate and rotate simultaneously.
- Appropriate clearances between interior surface 34 and outer surfaces 22 and 24, as well as, between shaft 28 and inner working surface 18 are important to the proper operation of the configuration.
- Preferred interferences between interior surface 34 and outer surfaces 22 and 24 of end portions 14 and 16 are in the range of .001 to .005 inches for housing structure bore diameters of approximately .25 inches to 2.50 inches.
- Typical clearances between the diameter of shaft 28 and the diameter of inner working surface 12 are nominally .004 inches for shaft diameters between .25 inches to about 2.50 inches. Too much clearance is detrimental to the efficient operation of the bearing. Chatter or noise can result as well as rough motion of the shaft. Clearance that is too small can cause shaft interference which is also non-beneficial to bearing operation.
- a preferred embodiment of this invention addresses these concerns.
- the diameter of outer surfaces 22 and 24 of end portions 14 and 16 is larger than interior surface 34 of housing structure 26. There exists a condition of interference between the two which is maintained within the preferable range of
- any reduction in diameter of inner working surface 12 is maintained below .003 inches to remain within the nominal clearance range of .001 to .004 inches for shafts less than .25 inches to about 2.5 inches.
- FIG. 4 shows a magnified cross-sectional view of end portion 16.
- End portion 16 is shown in an undeformed structure (solid lines) and a deformed structure (dashed lines).
- the solid lines represent end portion 16 prior to press- fitting bearing 10 into bore 26.
- bearing 10 When bearing 10 is pressed into housing structure 26 both inner surface 32 and outer surfaces 24 deform radially inward, filling at least part of the available space between inner surface 32 and shaft 28. Since only outer surface 24 of end portion 16 is in contact with housing bore 26, intermediate portion 12 is not loaded externally, and therefore does not substantially deform radially inward closing in the diameter of inner working surface 12. Therefore, a press-fit bearing arrangement is realized maintaining an appropriate clearance between shaft 28 and the inner working surface 12.
- Preferred material characteristics for bearing 10 include low-friction, low-wear, high strength and good performance at elevated temperatures. Materials with some flexibility are desired to undergo the deformation of press fitting without excessive stress. It is also desirable that the materials are resilient enough to hold their shape so that cold flow or creep does not present problems for the bearing.
- polymeric materials may be used in particular, polyamide (PA) including but not limited to nylon 6/6, polyphenylene sulfide (PPS) and polyphthalamide (PPA) thermoplastics.
- bearing 10 include end portions 14 and 16 having different diameters.
- FIG. 5 shows a cross-sectional view of housing structure 26 wherein interior surface 34 includes different diameters. It is also contemplated that end portions 14 and 16 can have different longitudinal lengths to accommodate varying housing structure sizes. It is further contemplated that intermediate portion 12 can have varied longitudinal lengths and diameters to accommodate varying housing structures.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mounting Of Bearings Or Others (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU11024/99A AU1102499A (en) | 1997-10-21 | 1998-10-20 | A plane bearing assembly |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US95483697A | 1997-10-21 | 1997-10-21 | |
US08/954,836 | 1997-10-21 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO1999020912A1 true WO1999020912A1 (en) | 1999-04-29 |
WO1999020912A9 WO1999020912A9 (en) | 2000-04-27 |
Family
ID=25495994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1998/022089 WO1999020912A1 (en) | 1997-10-21 | 1998-10-20 | A plane bearing assembly |
Country Status (2)
Country | Link |
---|---|
AU (1) | AU1102499A (en) |
WO (1) | WO1999020912A1 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004076872A1 (en) * | 2003-02-21 | 2004-09-10 | Tdw Delaware, Inc. | Sliding bearing subject to thermal expansion |
CN100412394C (en) * | 2003-02-21 | 2008-08-20 | Tdw特拉华有限公司 | Sliding bearing subject to thermal expansion |
WO2009133160A1 (en) * | 2008-04-30 | 2009-11-05 | Continental Teves Ag & Co. Ohg | Sliding bearing system comprising a bearing bushing, particularly for a motor vehicle brake |
EP2138731A1 (en) * | 2008-06-25 | 2009-12-30 | Robert Bosch Gmbh | Bearing bush and bearing |
DE102010023647A1 (en) * | 2010-06-14 | 2011-12-15 | Aktiebolaget Skf | Slide bearing component e.g. radial universal joint bearing, has sliding surface and sliding coating formed of sliding material, where sliding coating and support structure are mechanically connected with each other |
CN103986269A (en) * | 2014-04-09 | 2014-08-13 | 江苏一东航空机械有限公司 | Automobile wind-up window motor |
EP3173894A4 (en) * | 2014-07-25 | 2018-04-04 | Toyoda Iron Works Co., Ltd. | Bearing structure for vehicle pedal device and flanged bushing |
CN110352546A (en) * | 2017-03-09 | 2019-10-18 | 罗伯特·博世有限公司 | Particularly for the electric motor and transmission mechanism driving device of the comfortable driver in motor vehicle |
DE102018208478A1 (en) * | 2018-05-29 | 2019-12-05 | Zf Friedrichshafen Ag | Bearing bush for a pedal device of a motor vehicle and a pedal device with such a bearing bush |
AT522477B1 (en) * | 2019-06-06 | 2020-11-15 | Miba Gleitlager Austria Gmbh | Plain bearings with an exemption |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2675283A (en) | 1949-11-19 | 1954-04-13 | John B Thomson | Bearing |
DE1303587B (en) * | 1962-09-25 | 1972-03-09 | Landis & Gyr Ag | |
EP0272499A2 (en) * | 1986-12-19 | 1988-06-29 | International Business Machines Corporation | Bearing arrangement with bearing sleeve |
US4913562A (en) | 1989-01-06 | 1990-04-03 | Thomson Industries, Inc. | Thermoplastic bearing liner |
US5145265A (en) | 1991-10-18 | 1992-09-08 | Performance Plastics | Double flange pop-in bearing |
EP0558850A2 (en) * | 1992-03-05 | 1993-09-08 | Russell D. Ide | Self positioning beam mounted bearing and bearing and shaft assembly including the same |
US5358340A (en) * | 1993-09-20 | 1994-10-25 | Xerox Corporation | Bushing device for forming multiple pre-aligned bearing surface regions in a rotary assembly |
-
1998
- 1998-10-20 AU AU11024/99A patent/AU1102499A/en not_active Abandoned
- 1998-10-20 WO PCT/US1998/022089 patent/WO1999020912A1/en active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2675283A (en) | 1949-11-19 | 1954-04-13 | John B Thomson | Bearing |
DE1303587B (en) * | 1962-09-25 | 1972-03-09 | Landis & Gyr Ag | |
EP0272499A2 (en) * | 1986-12-19 | 1988-06-29 | International Business Machines Corporation | Bearing arrangement with bearing sleeve |
US4913562A (en) | 1989-01-06 | 1990-04-03 | Thomson Industries, Inc. | Thermoplastic bearing liner |
US5145265A (en) | 1991-10-18 | 1992-09-08 | Performance Plastics | Double flange pop-in bearing |
EP0558850A2 (en) * | 1992-03-05 | 1993-09-08 | Russell D. Ide | Self positioning beam mounted bearing and bearing and shaft assembly including the same |
US5358340A (en) * | 1993-09-20 | 1994-10-25 | Xerox Corporation | Bushing device for forming multiple pre-aligned bearing surface regions in a rotary assembly |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2004076872A1 (en) * | 2003-02-21 | 2004-09-10 | Tdw Delaware, Inc. | Sliding bearing subject to thermal expansion |
US7056027B2 (en) | 2003-02-21 | 2006-06-06 | Puckett Gregory L | Bearing for a rotatable shaft subject to thermal expansion |
CN100412394C (en) * | 2003-02-21 | 2008-08-20 | Tdw特拉华有限公司 | Sliding bearing subject to thermal expansion |
WO2009133160A1 (en) * | 2008-04-30 | 2009-11-05 | Continental Teves Ag & Co. Ohg | Sliding bearing system comprising a bearing bushing, particularly for a motor vehicle brake |
EP2138731A1 (en) * | 2008-06-25 | 2009-12-30 | Robert Bosch Gmbh | Bearing bush and bearing |
DE102010023647A1 (en) * | 2010-06-14 | 2011-12-15 | Aktiebolaget Skf | Slide bearing component e.g. radial universal joint bearing, has sliding surface and sliding coating formed of sliding material, where sliding coating and support structure are mechanically connected with each other |
CN103986269A (en) * | 2014-04-09 | 2014-08-13 | 江苏一东航空机械有限公司 | Automobile wind-up window motor |
EP3173894A4 (en) * | 2014-07-25 | 2018-04-04 | Toyoda Iron Works Co., Ltd. | Bearing structure for vehicle pedal device and flanged bushing |
CN110352546A (en) * | 2017-03-09 | 2019-10-18 | 罗伯特·博世有限公司 | Particularly for the electric motor and transmission mechanism driving device of the comfortable driver in motor vehicle |
DE102018208478A1 (en) * | 2018-05-29 | 2019-12-05 | Zf Friedrichshafen Ag | Bearing bush for a pedal device of a motor vehicle and a pedal device with such a bearing bush |
DE102018208478B4 (en) * | 2018-05-29 | 2021-05-06 | Zf Friedrichshafen Ag | Bearing bush for a pedal device of a motor vehicle and a pedal device with such a bearing bush |
AT522477B1 (en) * | 2019-06-06 | 2020-11-15 | Miba Gleitlager Austria Gmbh | Plain bearings with an exemption |
AT522477A4 (en) * | 2019-06-06 | 2020-11-15 | Miba Gleitlager Austria Gmbh | Plain bearings with an exemption |
Also Published As
Publication number | Publication date |
---|---|
AU1102499A (en) | 1999-05-10 |
WO1999020912A9 (en) | 2000-04-27 |
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