WO2010027918A1 - Palier de roulement pourvu d’éléments de distribution de lubrifiant disposés sur la bague de palier en rotation - Google Patents

Palier de roulement pourvu d’éléments de distribution de lubrifiant disposés sur la bague de palier en rotation Download PDF

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Publication number
WO2010027918A1
WO2010027918A1 PCT/US2009/055372 US2009055372W WO2010027918A1 WO 2010027918 A1 WO2010027918 A1 WO 2010027918A1 US 2009055372 W US2009055372 W US 2009055372W WO 2010027918 A1 WO2010027918 A1 WO 2010027918A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubrication
lubricant
race
rolling elements
deflecting
Prior art date
Application number
PCT/US2009/055372
Other languages
English (en)
Inventor
Dongbu Cao
Original Assignee
The Timken Company
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 The Timken Company filed Critical The Timken Company
Publication of WO2010027918A1 publication Critical patent/WO2010027918A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors

Definitions

  • the present invention is related generally to lubrication of rolling element (antifriction) bearings, and in particular, to internal structures within the rolling element bearings which are configured to facilitate a flow and delivery of lubricant into critical internal contact zones.
  • raceways will become depleted over time, and begin to accumulate elsewhere within the bearing structure or be ejected there from.
  • the present disclosure provides lubrication distribution structures within an antifriction bearing assembly adapted for facilitating rotation of components about an axis.
  • the bearing assembly generally comprises an outer race structure having a pair of raceway presented inwardly toward the axis of rotation, and an inner race structure having a pair of raceway presented outwardly toward the raceway of the outer race.
  • Rolling elements are organized in rows between, and contacting, each of the raceways of the outer and inner races, with a supply of lubricant located between the rows of rolling elements.
  • Lubricant distribution structures, in the form of deflecting surfaces are carried by one of the rotating races and are configured to deflect the migrating lubricant back towards the contact regions of the rolling elements and the raceway.
  • the lubricant distribution structures may be disposed medially, between the rows of rolling elements to direct a flow of lubricant outward towards each of the rows of rolling elements, may be disposed axially outboard of the rows of rolling elements to direct a flow of lubricant inward towards the rolling element contact regions, or may be disposed both medially between and axially outboard of the rows of rolling elements.
  • the lubricant distribution structures are in the form of angled fins extending radially from the rotating race in the annular region of the lubricant supply. Each of the fins is orientated to direct a flow of lubricant towards the rolling element contact regions upon rotation of the race in one direction.
  • the lubricant distribution structures are in the form of angled fins extending radially from the rotating race in the annular region of the lubricant supply. Each of the fins is orientated to direct a flow of lubricant towards the rolling element contact regions upon rotation of the race in either direction.
  • the lubricant distribution structures are in the form of wedge structures extending radially from the rotating race in the annular region of the lubricant supply. Each of the wedges is orientated to direct a flow of lubricant towards the rolling element contact regions upon rotation of the race in one direction.
  • the lubricant distribution structures are in the form of wedge structures extending radially from the rotating race in the annular region of the lubricant supply. Each of the wedges is orientated to direct a flow of lubricant towards the rolling element contact regions upon rotation of the race in either direction.
  • Figure 1 is a sectional view of a double-row tapered roller bearing of the present disclosure
  • Figure 2 is a sectional view of a bearing incorporating a fin-like structure of the present disclosure with grease deflecting surfaces disposed at the middle ring area between the two outer raceways;
  • Figure 3 is a partial plan view of a bearing cup incorporating a plurality of fin- like structures of Fig. 2;
  • Figure 4 is a sectional view of a bearing incorporating a solid triangular structure of the present disclosure with grease deflecting surfaces disposed at the middle ring area between the two outer raceways;
  • Figure 5 is a sectional view of a bearing incorporating a solid diamond-shaped structures of the present disclosure to provide bi-directional grease deflecting surfaces disposed at the middle ring area between the two outer raceways; and Figure 6 is an example of features that can propel lubricant into the raceway.
  • Corresponding reference numerals indicate corresponding parts throughout the several figures of the drawings. It is to be understood that the drawings are for illustrating the concepts set forth in the present disclosure and are not to scale. Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the drawings. DETAILED DESCRIPTION The following detailed description illustrates the invention by way of example and not by way of limitation.
  • an exemplary double row tapered roller bearing B generally incorporating lubrication distribution structures 100A and 100B is shown.
  • the bearing B which is organized about a rotational axis X, includes an outer race 2, a pair of inner races 4, separated at their front faces by a spacer 5, and rolling elements 6 in the form of tapered rollers arranged in two rows between raceways on the surfaces of the outer race 2 and the inner races 4, there being a separate row of rolling elements 6 around each inner race 4.
  • the bearing B may also have seals (not shown) at each axial end to enclose the spaces between the ends of the outer race 2 and the back face ends of the inner races 4, and thus isolate the interior of the bearing B from environmental contaminates and/or debris.
  • the outer race 2 has two tapered raceways 12 and an intervening medial surface 14 between the raceways 12. As seen in Figure 1 , with the use of tapered rollers, the raceways 12 each taper inwardly toward the intervening surface 14 and thus have their smallest diameters at the intervening surface 14, and their greatest diameters at the ends of the outer race 2.
  • Each inner race 4 includes a tapered raceway 18 and a thrust rib 20 at the large end of the raceway 18.
  • Each thrust rib 20 has a rib face 22 along the large end of the raceway 18 and is configured to prevent the rolling elements 6 from migrating up the raceways 12 and 18 and being expelled from the space between the outer race 2 and the inner races 4.
  • the two inner races 4 fit into opposite ends of the outer race 2, such that their respective raceways 18 are presented opposite the raceways 12 of the outer race 2.
  • the opposed raceways 12 and 18 of the outer race 2 and inner races 4 are inclined in the same direction, with the raceways 12 and 18 at one axial end of the bearing B being inclined inwardly in one direction and the raceways 12 and 18 at the other axial end of the bearing B being inclined downwardly in the opposite direction to form an indirect mounting arrangement.
  • the spacer ring 5 lies medially between, and separates the two inner races 4.
  • the spacer ring 5 abuts the small ends of the cones 4, with an axial width selected to establish a setting of the bearing B, which may be preload in which the bearing has no internal clearances, or may be end play.
  • the tapered rollers 6 are organized in two rows - one between the raceways
  • Contact zones which require lubrication include regions in which the tapered circumferential surfaces of the tapered rollers 6 contact the raceways 12 and 18 where the large end faces contact the rib faces 22 along the thrust ribs 20 of the two inner races 4.
  • the lubrication typically takes the form of grease.
  • the bearing B operates, that is to say when the outer race 2 rotates around the inner races 4 or the inner races 4 rotate in the outer race 2, the rolling elements 6 roll along the raceways 12 and 18 that confine them.
  • the rolling movement acts to pump the grease that is on the raceways 12 and 18 axially outward toward the thrust ribs 20 where it reduces friction between the large end faces 22 of the rolling elements 6 and the rib faces 22 on the thrust ribs 20.
  • the raceways 12 and 18 and the rib faces 22 will starve for lubrication, and while the bearing B may contain grease in the medial region between the intervening surface 14 of the outer race 2 and the spacer ring 5 that separates the two inner races 4, that grease may fail to migrate to the raceways 12 and 18 and to the large ends of the rollers 6.
  • at least one lubrication flow or deflecting structure 100 is attached to the outer race 2 on the intervening surface 14 between the two outer raceways 12.
  • each lubrication flow structure 100 consists of a pair of angled fins or vanes 102 defining lubrication deflecting surfaces aligned at a apex, which project radially inward from the intervening surface 14 into the annular volume between the inner and outer races.
  • the fins or vanes 102 of the lubrication flow structure 100 are aligned to define lubrication deflecting surfaces which directly displace or deflect grease or other lubricant from the medial annular region about the intervening surface 14 axially, outward into the contact regions of the raceways 12 and 18 on both sides of the bearing B when rotating in the direction of the apex of the deflecting surfaces 102.
  • While only one lubrication flow structure 100 is required, it is preferred that a plurality of structures 102 be aligned in a common orientation and disposed equidistantly about the circumference of the intervening surface 14, as shown in Figure 3.
  • a wake in the lubricant from the displacement enhances the lubricant circulation.
  • the motion of the lubricant flow structure 100 through the lubricant in the confined annular volume increases the fluidity of the lubricant by overcoming the lubricant's initial yield stress.
  • the lubricant maintains a desired immobility in areas of the bearing B which are not affected by the lubricant directly displaced by the lubricant flow structure 100.
  • the lubrication flow structures 100 may have a variety of configurations and/or surfaces for directly displacing or deflecting lubricant into the contact regions of the bearing B.
  • the lubrication flow structures 100 may be defined by raised solid triangular or wedge shaped elements 202 having angled deflecting surfaces 204 which project radially into the annular volume between the inner and outer races. Each element 202 extends radially inwardly into the lubricant flow domain illustrated in Fig. 2, and rotates with the outer race 2.
  • the rotating elements 202 directly displace lubricant from the annular volume adjacent the intervening surface 14 into the contact regions of the raceways 12 and 18 on both sides of the bearing B. While only one lubrication flow structure 100 is required, it is preferred that a plurality of elements 202 be aligned in a common orientation and disposed equidistantly about the circumference of the intervening surface 14.
  • the lubricant flow structures 100 may be configured to provide for the direct displacement of lubricant into the bearing contact regions upon rotation in either direction about the bearing axis.
  • the lubricant flow structures 100 disposed on the intervening surface 14 may be configured as raised solid or fined trapezoidal or diamond elements 302.
  • lubrication deflecting surfaces 304 define opposing wedges for direct displacement of lubricant from the medial annular volume adjacent the intervening surface into the contact regions of the raceways 12 and 18 on both sides of the bearing B during rotation of the supporting outer race 2 in either direction.
  • the specific shape and configuration of the lubricant flow structure 100 may be varied from the specific embodiments illustrated herein, provided that the shape and/or configuration utilized in the bearing B functions to directly displace lubricant accumulating in an annular region containing the lubricant flow structure 100 back into the contact regions of the bearing as the lubricant deflecting or flow structure 100 is carried by the rotating race.
  • Several exemplary shapes and configurations for lubricant flow structures 100 on the intermediate surface 14 are shown in Figure 6.
  • zig-zag elements 402 consisting of a plurality of radially projecting fins 404 arranged with alternating axial orientations
  • a sinusoidal element 502 consisting of a continuous radially projecting fin element 504 curved in a sinusoidal segment
  • the specific number of lubricant flow structures 100 utilized, as well as their size, length, and configuration, may be varied to accommodate the specific configuration of the supporting bearing B in which they are deployed.
  • lubricant deflecting or flow structures 100 While each of the aforementioned embodiments of the lubricant deflecting or flow structures 100 has been described as being disposed on the intervening surface 14 of a rotating outer race 2, it will be recognized that these lubricant deflecting or flow structures 100 may be disposed elsewhere within the bearing B on other rotating elements. For example, in supporting bearings B having rotating inner races 4, the lubricant flow structures 100 may be disposed on circumferential surface of the annular spacer 5, medially between each inner race 4, and oriented into the annular volume between the annular spacer 5 and the intervening surface 14 on the outer race 2.
  • lubricant flow structures 100 may, as shown in Figure 1 , be disposed on the rotating races 2 or 4 of the bearing B adjacent to the axial ends thereof, axially outward from the raceways 12 and 18. Lubricant flow structures 100 disposed in these areas must be configured to deflect any lubricant accumulating in the annular region axially outward from the raceways 12 and 18 in an axially inward direction towards the bearing contact regions.
  • lubricant flow structures 100 described herein have utility in connection with other types of bearings as well. These may include, but are not limited to, single row tapered roller bearings, both single and multiple row bearings, angular contact ball bearings, spherical roller bearings, and cylindrical roller bearings.

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

Abstract

L'invention porte sur un palier anti-frottement (B) incorporant des structures de déviation de lubrifiant (100). Le palier comprend une bague externe (2) dont le chemin de roulement (12) est dirigé intérieurement vers un axe de rotation (X) et une bague interne (4) dont le chemin de roulement (18) est dirigé extérieurement vers le chemin de roulement (12) de la bague externe (2). Des éléments de roulement (6) sont organisés dans au moins une rangée entre, et en contact, avec le chemin de roulement (12) de la bague externe (2) et le chemin de roulement interne (14) de la bague interne (4), un volume de lubrifiant étant localisé axialement adjacent aux éléments de roulement (6). Une ou plusieurs surfaces de déviation (102, 204) sont portées par au moins la bague en rotation dans la région du volume de lubrifiant, et sont configurées pour dévier le lubrifiant vers une région de contact des éléments de roulement (6) et des chemins de roulement (12, 14) lors de la rotation de la bague de support.
PCT/US2009/055372 2008-09-03 2009-08-28 Palier de roulement pourvu d’éléments de distribution de lubrifiant disposés sur la bague de palier en rotation WO2010027918A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US9380708P 2008-09-03 2008-09-03
US61/093,807 2008-09-03

Publications (1)

Publication Number Publication Date
WO2010027918A1 true WO2010027918A1 (fr) 2010-03-11

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016118058A1 (de) * 2016-09-23 2018-03-29 Thyssenkrupp Ag Wälzlager, Windkraftanlage und Verfahren zum Betrieb eines Wälzlagers
DE102019206268A1 (de) * 2019-05-02 2020-11-05 Volkswagen Aktiengesellschaft Nabenanordnung

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1913769A (en) * 1930-05-31 1933-06-13 Timken Roller Bearing Co Roller bearing
US3860302A (en) * 1973-06-29 1975-01-14 Woodrow W Gregg Ball bearing assembly
US4509869A (en) * 1983-11-10 1985-04-09 Johnston Kenneth R Self-greasing bearing
JPH0277106U (fr) * 1988-12-02 1990-06-13
US5312191A (en) * 1992-03-24 1994-05-17 S W Industries Lubrication mechanism for anti-friction bearings
DE4329398A1 (de) * 1993-01-13 1994-07-14 Ford Werke Ag Wälzlager
US5904427A (en) * 1996-11-04 1999-05-18 Stemco Inc Unitized wheel hub and bearing assembly with lubricant distributing vanes
US20070075581A1 (en) * 2005-10-04 2007-04-05 Slesinski Steven G Wheel hub lube director

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1913769A (en) * 1930-05-31 1933-06-13 Timken Roller Bearing Co Roller bearing
US3860302A (en) * 1973-06-29 1975-01-14 Woodrow W Gregg Ball bearing assembly
US4509869A (en) * 1983-11-10 1985-04-09 Johnston Kenneth R Self-greasing bearing
JPH0277106U (fr) * 1988-12-02 1990-06-13
US5312191A (en) * 1992-03-24 1994-05-17 S W Industries Lubrication mechanism for anti-friction bearings
DE4329398A1 (de) * 1993-01-13 1994-07-14 Ford Werke Ag Wälzlager
US5904427A (en) * 1996-11-04 1999-05-18 Stemco Inc Unitized wheel hub and bearing assembly with lubricant distributing vanes
US20070075581A1 (en) * 2005-10-04 2007-04-05 Slesinski Steven G Wheel hub lube director

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016118058A1 (de) * 2016-09-23 2018-03-29 Thyssenkrupp Ag Wälzlager, Windkraftanlage und Verfahren zum Betrieb eines Wälzlagers
DE102016118058B4 (de) * 2016-09-23 2019-02-14 Thyssenkrupp Ag Wälzlager und Windkraftanlage
DE102019206268A1 (de) * 2019-05-02 2020-11-05 Volkswagen Aktiengesellschaft Nabenanordnung

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