WO1996017179A1 - A roller bearing with curved rollers and race tracks - Google Patents

A roller bearing with curved rollers and race tracks Download PDF

Info

Publication number
WO1996017179A1
WO1996017179A1 PCT/SE1995/001435 SE9501435W WO9617179A1 WO 1996017179 A1 WO1996017179 A1 WO 1996017179A1 SE 9501435 W SE9501435 W SE 9501435W WO 9617179 A1 WO9617179 A1 WO 9617179A1
Authority
WO
WIPO (PCT)
Prior art keywords
rollers
roller
race
race tracks
bearing
Prior art date
Application number
PCT/SE1995/001435
Other languages
French (fr)
Inventor
Magnus Kellström
Peter ÅQVIST
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Priority to JP8518680A priority Critical patent/JPH10500199A/en
Priority to AU41917/96A priority patent/AU4191796A/en
Publication of WO1996017179A1 publication Critical patent/WO1996017179A1/en

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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers
    • 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
    • F16C19/36—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 a single row of rollers
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap

Definitions

  • the present invention refers to a roller bearing of the type defined in the preamble of claim 1.
  • Such bearings are known e.g. from US-A-2.595.121, which shows bearings with concave rollers and SE-A-53 256, which swows bearings with convex rollers.
  • the friction is lower in a bearing according to the preamble as compared to a spherical bearing with the same axial width, i.e. with equally long rollers.
  • a drawback is that the bearing, when equipped with common flanges and retainer, lacks the self-aligning ability of the spherical bearing, which ability is valuable in many situations. Furthermore it has hitherto been considered necessary to provide a roller mounting opening in one of the race rings, such as shown at reference numeral 8 in SE-A-53 256, for allowing insertion of a desired number of rollers in the bearing. Such an opening means a complication and reduces the usefulness, as the opening may not be situated in a loaded part of the bearing. If a mounting opening is missing in a known bearing of the above defined type, e.g. according to Fig.
  • EP-A-0 175 858 is described a roller bearing with cor ⁇ respondingly curved longitudinal section profiles at rollers and race tracks with a radius of curvature substantially bigger than the biggest distance between the centre axis of the bearing and the surfaces of the race tracks, whereby the rollers are axially movable between the race tracks without being obstructed by flanges or the like, for relative inclination and axial displaceability for the race tracks.
  • These specifications give good results regarding the load carrying capacity and adjustability, whereby as mentioned above the rollers at increased length, at the same time increase the load carrying capacity.
  • very flat rollers i.e.
  • the purpose of the present invention is to provide a bearing of the type defined in the preamble of claim 1, and in which has been obtained the best possible combination of the criteria; improved radial load carrying capacity, mutual misalignment and axial displacement of the bearing race tracks, and a good service life for the bearing. This is obtained in that the bearing has been given the characteriz ⁇ ing features defined in the accompanying claims.
  • Fig. 1 shows an axial section through a roller bearing according to the invention
  • Fig. 2 is a roller forming part of the bearing according to Fig. 1, shown with load and force lines, and Fig. 3 illustrates in an axial section one half of an angular contact roller bearing according to the invention.
  • Fig. 1 shows schematically a cross section through a bearing 1, incorporating an inner race ring 2 having an outer race track 3, and an outer race ring 4 with an inner race track 5. Between the race tracks 3 and 5 are provided a number of rollers 6.
  • the inner race ring 2 is fixedly connected to a shaft 7 in a manner not further shown, and which shaft in the position shown, i.a. due to the deflection of the shaft and the direction of the load acting upon the bearing, is misaligned under an angle ⁇ against the centre axis 8 of the bearing.
  • the rings 2 and 4 will obtain a mutual misalignment ⁇ , whereby the rollers 6 have a possibility to move axially for compensating this misalignment.
  • the smooth curvature of the surfaces permits that the radial extension of the bearing, required for a given roller length is small, which is space-saving, and that the internal friction appearing in the bearing, due to sliding at contact between rollers and race track, is low as compared to the case in spherical roller bearings with a corresponding load carrying capacity and subjected to corresponding load.
  • Fig. 2 a roller 6 forming part of the bearing according to Fig. 1, and having a radius of curvature R for the longituduinal section profile.
  • a load Q acts upon the roller under the angle ⁇ , due to the the fact that the roller slides axially at misalignment and the friction force thereby generated must be balanced by the normal forces of the roller.
  • the axial displacement of the force on the roller can be expressed as the distance ⁇ between a line perpendicular to the centre axis of the roller at the middle of the roller and the point where the load Q attacks the roller.
  • ⁇ must be smaller than half the length of the roller, i.e. l a /2.
  • Fig. 3 is shown an axial cross section of one half of an angular contact roller bearing with an inner race ring 12 with a curved race track, which is inclined against the centre line 18 of the bearing and an outer race ring 14 likewise having a curved race track inclined against the centre line 18 of the bearing.
  • crowned rollers 6 which are not obstructed from moving axially by flanges or retainer, and which like the race tracks have a longitudinal section profile with a radius of curvature R, which is bigger than the distance between the outer race track and the axis of the bearing, measured perpendicularly to the race track.

Abstract

Roller bearing incorporating a number of rollers (6) provided between and in contact with two race tracks (3, 5), whereby the rollers and the race tracks have longitudinal section profiles with substantially the same radius of curvature (R), and where the radius of curvature (R) is bigger than the distance between the outer race track and the axis of the bearing, measured perpendicularly against the race track, whereby the rollers (6) are axially movable between the race tracks without obstructions from axial limitations at the race tracks for permitting relative misalignment and axial displaceability of the race tracks, which are only limited by the radial squeezing of the rollers between the race tracks, wherein the relation between the radius of curvature (R) of the roller profile and the length of the roller (1a) is R/1a < 20.

Description

A roller bearing with curved rollers and race tracks
The present invention refers to a roller bearing of the type defined in the preamble of claim 1.
Such bearings are known e.g. from US-A-2.595.121, which shows bearings with concave rollers and SE-A-53 256, which swows bearings with convex rollers. As the radii of the profile curve of race tracks and rollers in such bearings are substantially bigger than the corresponding radii e.g. in spherical roller bearings with corresponding radial dimensions, it is possible to make the rollers longer than what is possible in such spherical bearings, and this improves the radial load carrying capacity. Furthermore the friction is lower in a bearing according to the preamble as compared to a spherical bearing with the same axial width, i.e. with equally long rollers. A drawback is that the bearing, when equipped with common flanges and retainer, lacks the self-aligning ability of the spherical bearing, which ability is valuable in many situations. Furthermore it has hitherto been considered necessary to provide a roller mounting opening in one of the race rings, such as shown at reference numeral 8 in SE-A-53 256, for allowing insertion of a desired number of rollers in the bearing. Such an opening means a complication and reduces the usefulness, as the opening may not be situated in a loaded part of the bearing. If a mounting opening is missing in a known bearing of the above defined type, e.g. according to Fig. 8 of the above mentioned US patent, it is necessary to provide the bearing with rollers during the time the outer and inner race rings are positioned eccentrically, which allows filling of the bearing with a comparatively small number of rollers. Such a bearing therefore has a comparatively low load carrying capacity.
In EP-A-0 175 858 is described a roller bearing with cor¬ respondingly curved longitudinal section profiles at rollers and race tracks with a radius of curvature substantially bigger than the biggest distance between the centre axis of the bearing and the surfaces of the race tracks, whereby the rollers are axially movable between the race tracks without being obstructed by flanges or the like, for relative inclination and axial displaceability for the race tracks. These specifications give good results regarding the load carrying capacity and adjustability, whereby as mentioned above the rollers at increased length, at the same time increase the load carrying capacity. However it has proven itself that very flat rollers, i.e. having a large ratio between the curvature radius of the roller profile and the roller length, will give the bearing a shorter service life, due to high edge pressures, i.e. high pressures at the end of the roller, which means that such bearings, which have very high load carrying capacity, will get unacceptably reduced life span at misalignment.
The purpose of the present invention is to provide a bearing of the type defined in the preamble of claim 1, and in which has been obtained the best possible combination of the criteria; improved radial load carrying capacity, mutual misalignment and axial displacement of the bearing race tracks, and a good service life for the bearing. This is obtained in that the bearing has been given the characteriz¬ ing features defined in the accompanying claims.
Hereinafter the invention will be described with reference to two embodiments shown in the accompanying drawings.
Fig. 1 shows an axial section through a roller bearing according to the invention,
Fig. 2 is a roller forming part of the bearing according to Fig. 1, shown with load and force lines, and Fig. 3 illustrates in an axial section one half of an angular contact roller bearing according to the invention.
Fig. 1 shows schematically a cross section through a bearing 1, incorporating an inner race ring 2 having an outer race track 3, and an outer race ring 4 with an inner race track 5. Between the race tracks 3 and 5 are provided a number of rollers 6. The inner race ring 2 is fixedly connected to a shaft 7 in a manner not further shown, and which shaft in the position shown, i.a. due to the deflection of the shaft and the direction of the load acting upon the bearing, is misaligned under an angle γ against the centre axis 8 of the bearing. Hereby also the rings 2 and 4 will obtain a mutual misalignment γ, whereby the rollers 6 have a possibility to move axially for compensating this misalignment. The rollers 6, as well as the race tracks 3 and 5 resp. hereby have a longitudinal section profile, with a radius R of curvature bigger than the biggest distance between the centre axis of the bearing and the race track surfaces. The smooth curvature of the surfaces permits that the radial extension of the bearing, required for a given roller length is small, which is space-saving, and that the internal friction appearing in the bearing, due to sliding at contact between rollers and race track, is low as compared to the case in spherical roller bearings with a corresponding load carrying capacity and subjected to corresponding load.
In Fig. 2 is shown a roller 6 forming part of the bearing according to Fig. 1, and having a radius of curvature R for the longituduinal section profile. At misalignment in accordance with Fig. 1 a load Q acts upon the roller under the angle φ, due to the the fact that the roller slides axially at misalignment and the friction force thereby generated must be balanced by the normal forces of the roller.
When the load Q in such a bearing acts against the roller due to the inner and outer ring contact under the angle φ against a line ' through the centre of the roller perpendicularly to the roller axis, it is obtained a radial and an axial force component.
The axial force acting from a race track on the roller will be Q sin cp , which at the small angles, here concerned, can be simplified to Q φ. The roller thereby is subjected to a combined axial force from both race tracks, which can be expressed 2 Q φ. For the roller in axial equilibrium accord¬ ing to the equilibrium equation is valid
2 Q φ = μ Q (equ. I) wherein μ = the coefficient of friction between the roller 6 and its cooperating race track. This friction coefficient is by experience typically between 0.05 and 0.1, depending on the lubrication conditions.
The force lines in the drawing are drawn just opposite each other, whereas they in practice are displaced axially a small distance relative to each other.
The axial displacement of the force on the roller can be expressed as the distance Δ between a line perpendicular to the centre axis of the roller at the middle of the roller and the point where the load Q attacks the roller. The geometri¬ cal relation for this condition is φ = Δ / R (equ. II)
After reduction of equation I is obtained φ = μ/2 (equ. Ill)
By inserting equation III into equation II is obtained
Δ = μ R/2 (equ. IV)
At the same time it is evident that Δ must be smaller than half the length of the roller, i.e. la/2.
Therefrom it follows that μ R/2 < la/2 (equ. V)
From this relation it is also obtained that
R/l. < l./μ (equ. VI)
At the above mentioned lowest value for μ of about 0.05, which is established by way of experience, is obtained a limit value for the relation between the radius of curvature R for the roller and the length of the roller la, i.e. R/la, which is over 20. Over this value the bearing will not function well, as extreme edge pressures will appear at misalignment, leading to a short life span. The relation therefore must be
R/la < 20 (equ. VII)
In Fig. 3 is shown an axial cross section of one half of an angular contact roller bearing with an inner race ring 12 with a curved race track, which is inclined against the centre line 18 of the bearing and an outer race ring 14 likewise having a curved race track inclined against the centre line 18 of the bearing. Between the race tracks in the race rings 12, 14 are provided crowned rollers 6, which are not obstructed from moving axially by flanges or retainer, and which like the race tracks have a longitudinal section profile with a radius of curvature R, which is bigger than the distance between the outer race track and the axis of the bearing, measured perpendicularly to the race track.
The same forces as illustrated in Fig. 2 act upon the rollers in such a bearing, and the same relation reigns between the radius of curvature of the longitudinal section profile and the roller length as in this case.
The invention is not limited to the embodiment shown and described in connection thereto but modifications and variations can appear within the scope of the corresponding claims.

Claims

CLAIM
Roller bearing incorporating a number of rollers (6) provided between and in contact with two race tracks (3, 5), whereby the rollers and the race tracks have longitudinal section profiles with substantially the same radius of curvature (R), and where the radius of curvature (R) is bigger than the distance between the outer race track and the axis of the bearing, measured perpendicularly against the race track, whereby the rollers (6) are axially movable between the race tracks without obstructions from axial limitations at the race tracks for permitting relative misalignment and axial displaceability of the race tracks, which are only limited by the radial squeezing of the rollers between the race tracks, c h a r a c t e r i z e d t h e r e i n, that the relation between the radius of curvature (R) of the roller profile and the length of the roller (la) is
R/l. < 20.
PCT/SE1995/001435 1994-12-02 1995-11-30 A roller bearing with curved rollers and race tracks WO1996017179A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP8518680A JPH10500199A (en) 1994-12-02 1995-11-30 Roller bearing
AU41917/96A AU4191796A (en) 1994-12-02 1995-11-30 A roller bearing with curved rollers and race tracks

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9404217-3 1994-12-02
SE9404217A SE9404217L (en) 1994-12-02 1994-12-02 Roller bearing

Publications (1)

Publication Number Publication Date
WO1996017179A1 true WO1996017179A1 (en) 1996-06-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1995/001435 WO1996017179A1 (en) 1994-12-02 1995-11-30 A roller bearing with curved rollers and race tracks

Country Status (7)

Country Link
JP (1) JPH10500199A (en)
CN (1) CN1168717A (en)
AR (1) AR000273A1 (en)
AU (1) AU4191796A (en)
SE (1) SE9404217L (en)
WO (1) WO1996017179A1 (en)
ZA (1) ZA9510055B (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6315458B1 (en) 1998-06-19 2001-11-13 Nsk Ltd. Roller bearing
US6354745B1 (en) 1999-09-16 2002-03-12 The Timken Company Fully self-aligning roller bearing
US6709164B2 (en) 2001-04-12 2004-03-23 Nsk Ltd. Tapered roller bearing
DE19612589B4 (en) * 1996-03-29 2005-12-22 Skf Gmbh storage
DE102005058149A1 (en) * 2005-12-06 2007-07-05 Schaeffler Kg Tapered roller bearings with curved raceways
CZ302961B6 (en) * 2010-12-01 2012-01-25 ZKL - Výzkum a vývoj, a.s. Mounting of output shaft for driving large-volume rotary tanks with inclined axis of rotation
US9261132B2 (en) 2009-04-24 2016-02-16 Roller Bearing Company Of America, Inc. Low friction bearing assembly and link apparatus
EP3020987A1 (en) * 2014-11-13 2016-05-18 Aktiebolaget SKF Angular contact self-aligning toroidal rolling element bearing
US10023302B2 (en) 2007-12-06 2018-07-17 Roller Bearing Company Of America, Inc. Actuation system for a lift assisting device and lined track rollers used therein
US11149788B2 (en) 2012-04-30 2021-10-19 Roller Bearing Company Of America, Inc. Hybrid bearing assembly with rolling elements and plain bearing

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20120091470A (en) * 2004-02-19 2012-08-17 가부시키가이샤 제이텍트 Tapered roller bearing
US20150098825A1 (en) * 2012-04-23 2015-04-09 Hans Wendeberg Bearing arrangement
JP2015514949A (en) * 2012-04-23 2015-05-21 アクティエボラゲット・エスコーエッフ Toroidal roller bearing
CN103807301A (en) * 2013-12-27 2014-05-21 瓦房店轴承集团有限责任公司 Bearing with special patching structure

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE449908B (en) * 1984-09-26 1987-05-25 Skf Ab ROLLER BEARINGS WHERE THE ROLLERS AND ROPES ARE CROSSED LENGTH CROSS PROFILES
EP0383027A1 (en) * 1989-02-15 1990-08-22 JACOB, Werner Self-aligning bearing

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE449908B (en) * 1984-09-26 1987-05-25 Skf Ab ROLLER BEARINGS WHERE THE ROLLERS AND ROPES ARE CROSSED LENGTH CROSS PROFILES
EP0383027A1 (en) * 1989-02-15 1990-08-22 JACOB, Werner Self-aligning bearing

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612589B4 (en) * 1996-03-29 2005-12-22 Skf Gmbh storage
US6315458B1 (en) 1998-06-19 2001-11-13 Nsk Ltd. Roller bearing
US6354745B1 (en) 1999-09-16 2002-03-12 The Timken Company Fully self-aligning roller bearing
US6709164B2 (en) 2001-04-12 2004-03-23 Nsk Ltd. Tapered roller bearing
DE102005058149A1 (en) * 2005-12-06 2007-07-05 Schaeffler Kg Tapered roller bearings with curved raceways
US10023302B2 (en) 2007-12-06 2018-07-17 Roller Bearing Company Of America, Inc. Actuation system for a lift assisting device and lined track rollers used therein
US9261132B2 (en) 2009-04-24 2016-02-16 Roller Bearing Company Of America, Inc. Low friction bearing assembly and link apparatus
CZ302961B6 (en) * 2010-12-01 2012-01-25 ZKL - Výzkum a vývoj, a.s. Mounting of output shaft for driving large-volume rotary tanks with inclined axis of rotation
US11149788B2 (en) 2012-04-30 2021-10-19 Roller Bearing Company Of America, Inc. Hybrid bearing assembly with rolling elements and plain bearing
EP3020987A1 (en) * 2014-11-13 2016-05-18 Aktiebolaget SKF Angular contact self-aligning toroidal rolling element bearing
US9784309B2 (en) 2014-11-13 2017-10-10 Aktiebolaget Skf Angular contact self-aligning toroidal rolling element bearing

Also Published As

Publication number Publication date
ZA9510055B (en) 1996-06-06
SE9404217L (en) 1996-06-03
CN1168717A (en) 1997-12-24
AR000273A1 (en) 1997-06-18
SE9404217D0 (en) 1994-12-02
AU4191796A (en) 1996-06-19
JPH10500199A (en) 1998-01-06

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