WO2012135254A1 - Bearing lubrication passage - Google Patents

Bearing lubrication passage Download PDF

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Publication number
WO2012135254A1
WO2012135254A1 PCT/US2012/030800 US2012030800W WO2012135254A1 WO 2012135254 A1 WO2012135254 A1 WO 2012135254A1 US 2012030800 W US2012030800 W US 2012030800W WO 2012135254 A1 WO2012135254 A1 WO 2012135254A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
lubricant
axially
bearing assembly
race
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/US2012/030800
Other languages
French (fr)
Inventor
Gerald P. Fox
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 WO2012135254A1 publication Critical patent/WO2012135254A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6685—Details of collecting or draining, e.g. returning the liquid to a sump
    • 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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller 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
    • 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
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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 bearing lubrication systems, and in particular, to a bearing lubricant replenishment system disposed within the stationary bearing race(s) of a sealed bearing having a stationary inner race and a rotating outer race, in which a seal mounting surface rotates with the outer race, and a seal lip rides on an outside diameter of a stationary bearing flange adjacent one end of the rollers, maintaining a narrow bearing width.
  • Wind energy main shaft bearings are often equipped with outboard seals that are integrated, in varying degrees, into the bearing.
  • One such prior art integrated design for use in wind turbines is shown in Figure 1 , is often referred to as a tapered double outer (TDO) bearing (1 ) where the inner bearing races (2) are stationary, while the double outer bearing race (3) rotates with the wind turbine rotor and nose cone system (or other rotating structure supported by the bearing (1 )).
  • the conventional lubricant delivery system disposed within this style of bearing is less than ideal.
  • a seal (4) is mounted in a rotating seal carrier (5) having lubricant circulation or purge holes (6) through which a flow of lubricant may circulate.
  • a lip (7) of the seal (4) rides directly on an outer diameter surface (8) of a large end flange (2A) of the stationary inner bearing race (2).
  • the usual lubricant introduction and replenishment path injects fresh lubricant through a central passage (9) in a stationary spacer (10) disposed between the inner bearing races (2), and purges used lubricant through the lubricant circulation or purge holes (6) in the rotating seal carrier (5).
  • Purging used lubricant through the rotating components of the bearing (1 ) is not ideal because the used lubricant must be subsequently collected and stored in the rotating part of the bearing system until it can be manually disposed of.
  • a bearing assembly configured with a lubrication system which introduces new lubricant, and which purges used lubricant, through the stationary bearing race, but which does not significantly increase the overall width, weight, or material cost of the bearing assembly.
  • the present disclosure provides a sealed bearing having a rotating outer race and a stationary inner race with bearing lubrication passages disposed within the stationary inner race for the delivery of fresh lubricant and for the purging of used lubricant without increasing the axial width of the sealed bearing.
  • a central lubricant delivery passage is disposed in a stationary inner race of the bearing, to deliver a supply of fresh lubricant to a central annular space between adjacent rows of rolling elements within the bearing.
  • At least one axially-aligned lubricant discharge passage is provided through the axially outer flange of the stationary inner race, intersecting a radial discharge passage to provide a lubricant discharge pathway contained within the radial footprint of an associated bearing seal.
  • a central lubricant discharge passage is disposed in a stationary inner race of the bearing, to discharge used lubricant from the central annular space between adjacent rows of rolling elements within the bearing.
  • At least one axially-aligned lubricant delivery passage is provided through the axially outer flange of the stationary inner race, intersecting a radial delivery passage to provide a lubricant delivery pathway contained within the radial footprint of an associated bearing seal through, which fresh lubricant can be delivered into the internal volume of the bearing.
  • Figure 1 is a sectional view of a prior art bearing assembly having a lubricant discharge passage through the rotating seal carrier;
  • Figure 2 is a sectional view of a prior art bearing assembly having a lubricant discharge passage at the outer diameter of the stationary inner race, adjacent to the bearing axial seal surfaces;
  • Figure 3 is a sectional view of a bearing assembly configured with a lubrication passage of the present invention, axially intersecting the outer flange of the stationary inner race.
  • a first embodiment of the present disclosure is shown generally as a bearing assembly (A) having stationary inner races (2) and a rotating outer race (3).
  • the inner races (2) be disposed in butting engagement with the central spacer (2B).
  • the bearing assembly (A) is a sealed bearing, with two rows of rolling elements (RE) disposed between the inner and outer races, and axially enclosed by seals (4) supported on seal carriers (5) which are secured to, and rotate with, the rotating outer race (3).
  • the seals (4) each have seal lips (7) which are generally in sealing contact with an outer surface (8) of each adjacent inner race (2).
  • a lubrication passage (12) is provided radially through the outer peripheral end of each of the bearing stationary inner races (2) within the radial footprint of each seal (4), which can be considered to be a projection radially inward of the contact region between the seal lips (7) and the outer surface (8).
  • Each lubrication passage (12) intersects with an passage (13) aligned parallel to the bearing axis of rotation, within the flange region (2A) of the inner race, radially adjacent to the inner race outer surface (8).
  • Each axial passage (13) opens into an outer chamber (17) of the bearing (2) on an inboard axial face (14) of the flange (2A), and not on the outer circumferential surface (8) of the flange (2A).
  • Each axial passage (13) may optionally extend to an axially outboard end of the inner race flange (2A) where it is closed by a plug (P) or other suitable closure means.
  • each flange (2A) is elongated in a radial direction, relative to the prior art such as shown in Figs. 1 and 2, while the axial width of the flange, and therefore, the overall axial width of the bearing (A), remains unchanged.
  • fresh lubricant is circulated through the bearing assembly (A) of Figure 3 in one of two directions.
  • the first preferred direction utilizes a natural pumping action of the bearing rolling elements (RE) to impart a flow to lubricant delivered through passage (9) in the central spacer (2B) to the bearing center chamber (16) axially outward towards one or the other of the bearing's two outer chambers (17), and injects fresh lubricant into the bearing's center chamber (16) through passage (9).
  • the fresh lubricant is circulated around, and passed over the rolling elements (RE), into the axially outer chambers (17), where it is discharged through axial passages (13) into radial passages (12) in the stationary inner races (2).
  • the second direction in which the fresh lubricant is circulated through the bearing assembly (A) of Figure 3 is the opposite of the first preferred direction described above.
  • fresh lubricant is injected into the bearing assembly through the radial passages (12) discharged into the outer chambers (17) through the axial passages (13) in the axial faces (14) of the flanges (2A).
  • the fresh lubricant will accumulate in these chambers and around the rolling elements (RE), until a sufficient volume of fresh lubricant has been introduced into the outer chambers (17) to push older lubricant past the rolling elements (RE) and into the center chamber (16), where one or more generously sized purge ports (19) in the central spacer (2B) having a diameter which is greater than that of the passages (9), permit the used lubricant to be easily purged or discharged from the bearing assembly (A) through the stationary inner races (2).
  • the bearing assembly (A) employ seals (4) which have a minimum section height to compensate as much as possible for the required increase in the overall diameter of the bearing flange (2A) to accommodate the radial passages (12) and axial passages (13).
  • seals (4) which have a minimum section height to compensate as much as possible for the required increase in the overall diameter of the bearing flange (2A) to accommodate the radial passages (12) and axial passages (13).
  • the bolt circle (20) in the bearing rotating outer race can be kept as small as possible, thus allowing smaller diameter (and less costly) components to be secured to the bearing assembly (A).

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

Abstract

A bearing assembly (A) having stationary inner races (2) and a rotating outer race (3), is configured with rolling elements (RE) disposed between the inner and outer races, and axially enclosed by seals (4) supported on seal carriers (5) which are secured to, and rotate with, the rotating outer race. A lubrication passage (12) is provided radially through each bearing stationary inner race to open into an outer portion (17) of the bearing chamber, at an axial face (14) of an outboard flange (2A) of the inner race. The outer diameter of the outboard flange (2A) is enlarged in a radial direction, to accommodate the lubrication passage opening on the axial face, while an axial width of the outboard flange, and therefore, the overall axial width of the bearing, remains unchanged.

Description

B EARING LUBRICATION PASSAGE
CROSS-REFERENCE TO RELATED APPLICATIONS
The present application is related to, and claims priority from, U.S. Provisional Patent Application Serial No. 61 /468,260 filed on March 28, 201 1 , which is herein incorporated by reference.
STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH
Not Applicable.
BACKGROUND OF THE INVENTION
The present invention is related generally to bearing lubrication systems, and in particular, to a bearing lubricant replenishment system disposed within the stationary bearing race(s) of a sealed bearing having a stationary inner race and a rotating outer race, in which a seal mounting surface rotates with the outer race, and a seal lip rides on an outside diameter of a stationary bearing flange adjacent one end of the rollers, maintaining a narrow bearing width.
Wind energy main shaft bearings (and many other bearings) are often equipped with outboard seals that are integrated, in varying degrees, into the bearing. One such prior art integrated design for use in wind turbines is shown in Figure 1 , is often referred to as a tapered double outer (TDO) bearing (1 ) where the inner bearing races (2) are stationary, while the double outer bearing race (3) rotates with the wind turbine rotor and nose cone system (or other rotating structure supported by the bearing (1 )). The conventional lubricant delivery system disposed within this style of bearing is less than ideal. A seal (4) is mounted in a rotating seal carrier (5) having lubricant circulation or purge holes (6) through which a flow of lubricant may circulate. A lip (7) of the seal (4) rides directly on an outer diameter surface (8) of a large end flange (2A) of the stationary inner bearing race (2). With this configuration, the usual lubricant introduction and replenishment path injects fresh lubricant through a central passage (9) in a stationary spacer (10) disposed between the inner bearing races (2), and purges used lubricant through the lubricant circulation or purge holes (6) in the rotating seal carrier (5). Purging used lubricant through the rotating components of the bearing (1 ) is not ideal because the used lubricant must be subsequently collected and stored in the rotating part of the bearing system until it can be manually disposed of.
In an alternate prior art configuration shown in Figure 2, used lubricant is purged and collected through passages (1 1 ) in the stationary bearing races (2) of a bearing (1 ). With this configuration, radial passages (1 1 ) are drilled from inside the stationary bearing race (2) to the outer diameter surface (8) but to do so, the overall bearing width must be increased to accommodate both the radial passage, variations in size and axial position, and the seal lip and its variation in size and axial position. The bearing configuration shown in Figure 2 necessarily adds to the bearing width, weight, and material cost.
Accordingly, it would be advantageous to provide a bearing assembly configured with a lubrication system which introduces new lubricant, and which purges used lubricant, through the stationary bearing race, but which does not significantly increase the overall width, weight, or material cost of the bearing assembly.
BRIEF SUMMARY OF THE INVENTION
Briefly stated, the present disclosure provides a sealed bearing having a rotating outer race and a stationary inner race with bearing lubrication passages disposed within the stationary inner race for the delivery of fresh lubricant and for the purging of used lubricant without increasing the axial width of the sealed bearing.
In a first embodiment, a central lubricant delivery passage is disposed in a stationary inner race of the bearing, to deliver a supply of fresh lubricant to a central annular space between adjacent rows of rolling elements within the bearing. At least one axially-aligned lubricant discharge passage is provided through the axially outer flange of the stationary inner race, intersecting a radial discharge passage to provide a lubricant discharge pathway contained within the radial footprint of an associated bearing seal.
In a second embodiment, a central lubricant discharge passage is disposed in a stationary inner race of the bearing, to discharge used lubricant from the central annular space between adjacent rows of rolling elements within the bearing. At least one axially-aligned lubricant delivery passage is provided through the axially outer flange of the stationary inner race, intersecting a radial delivery passage to provide a lubricant delivery pathway contained within the radial footprint of an associated bearing seal through, which fresh lubricant can be delivered into the internal volume of the bearing.
The foregoing features, and advantages set forth in the present disclosure as well as presently preferred embodiments will become more apparent from the reading of the following description in connection with the accompanying drawings.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS
In the accompanying drawings which form part of the specification:
Figure 1 is a sectional view of a prior art bearing assembly having a lubricant discharge passage through the rotating seal carrier;
Figure 2 is a sectional view of a prior art bearing assembly having a lubricant discharge passage at the outer diameter of the stationary inner race, adjacent to the bearing axial seal surfaces; and
Figure 3 is a sectional view of a bearing assembly configured with a lubrication passage of the present invention, axially intersecting the outer flange of the stationary inner race.
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. The description enables one skilled in the art to make and use the present disclosure, and describes several embodiments, adaptations, variations, alternatives, and uses of the present disclosure, including what is presently believed to be the best mode of carrying out the present disclosure.
Turning to Figure 3, a first embodiment of the present disclosure is shown generally as a bearing assembly (A) having stationary inner races (2) and a rotating outer race (3). The inner races (2) be disposed in butting engagement with the central spacer (2B). The bearing assembly (A) is a sealed bearing, with two rows of rolling elements (RE) disposed between the inner and outer races, and axially enclosed by seals (4) supported on seal carriers (5) which are secured to, and rotate with, the rotating outer race (3). The seals (4) each have seal lips (7) which are generally in sealing contact with an outer surface (8) of each adjacent inner race (2).
As seen in Figure 3, a lubrication passage (12) is provided radially through the outer peripheral end of each of the bearing stationary inner races (2) within the radial footprint of each seal (4), which can be considered to be a projection radially inward of the contact region between the seal lips (7) and the outer surface (8). Each lubrication passage (12) intersects with an passage (13) aligned parallel to the bearing axis of rotation, within the flange region (2A) of the inner race, radially adjacent to the inner race outer surface (8). Each axial passage (13) opens into an outer chamber (17) of the bearing (2) on an inboard axial face (14) of the flange (2A), and not on the outer circumferential surface (8) of the flange (2A). Each axial passage (13) may optionally extend to an axially outboard end of the inner race flange (2A) where it is closed by a plug (P) or other suitable closure means. In order to provide sufficient surface area for the opening of the axial passage (13), each flange (2A) is elongated in a radial direction, relative to the prior art such as shown in Figs. 1 and 2, while the axial width of the flange, and therefore, the overall axial width of the bearing (A), remains unchanged.
During operation, fresh lubricant is circulated through the bearing assembly (A) of Figure 3 in one of two directions. The first preferred direction utilizes a natural pumping action of the bearing rolling elements (RE) to impart a flow to lubricant delivered through passage (9) in the central spacer (2B) to the bearing center chamber (16) axially outward towards one or the other of the bearing's two outer chambers (17), and injects fresh lubricant into the bearing's center chamber (16) through passage (9). The fresh lubricant is circulated around, and passed over the rolling elements (RE), into the axially outer chambers (17), where it is discharged through axial passages (13) into radial passages (12) in the stationary inner races (2). Those of ordinary skill in the art will readily recognize that the size of the passages (12) and (13), as well as the total number of identical passages disposed about the circumference of the bearing assembly (A), which can be more than one, provide sufficient area and volume for the used lubricant to discharge freely.
The second direction in which the fresh lubricant is circulated through the bearing assembly (A) of Figure 3 is the opposite of the first preferred direction described above. In the second direction, fresh lubricant is injected into the bearing assembly through the radial passages (12) discharged into the outer chambers (17) through the axial passages (13) in the axial faces (14) of the flanges (2A). The fresh lubricant will accumulate in these chambers and around the rolling elements (RE), until a sufficient volume of fresh lubricant has been introduced into the outer chambers (17) to push older lubricant past the rolling elements (RE) and into the center chamber (16), where one or more generously sized purge ports (19) in the central spacer (2B) having a diameter which is greater than that of the passages (9), permit the used lubricant to be easily purged or discharged from the bearing assembly (A) through the stationary inner races (2).
In either case, it is preferred that the bearing assembly (A) employ seals (4) which have a minimum section height to compensate as much as possible for the required increase in the overall diameter of the bearing flange (2A) to accommodate the radial passages (12) and axial passages (13). Similarly, by minimizing the outer diameter of the seal carrier (5) as much as possible, the bolt circle (20) in the bearing rotating outer race can be kept as small as possible, thus allowing smaller diameter (and less costly) components to be secured to the bearing assembly (A).
As various changes could be made in the above constructions without departing from the scope of the disclosure, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.

Claims

CLAIMS:
1. An improved sealed bearing assembly (A) having a pair of stationary inner races (2) and a rotating outer race (3), with two rows of rolling elements (RE) disposed with a bearing chamber between the inner and outer races, axially enclosed by seals (4) supported on seal carriers (5) which are secured to, and rotate with, the rotating outer race, the improvement comprising:
a lubrication passage (12) disposed in each of the stationary inner races, said lubrication passage in fluid communication with an opening at an axial inboard face (14) of a radially-extending flange (2A) within the bearing chamber, adjacent to an axially outboard end of the inner race.
2. The improved sealed bearing assembly (A) of Claim 1 wherein said seals have seal lips (7) which are in sealing contact with an outer circumferential surface (8) of the radially-extending flange (2A) of the stationary inner races.
3. The improved bearing assembly of Claim 1 wherein said lubrication passage (12) extends radially from an inner circumferential surface of the inner race to intersect an axial passage (13) radially inboard from an outer circumferential surface (8) of the radially-extending flange (2A), said axial passage (13) defining said opening at said axial inboard face (14) of the radially-extending flange (2A).
4. The improved bearing assembly of Claim 3 wherein said axial passage (13) extends to an axially outboard end of said inner race flange (2A), and wherein said axial passage (13) is sealed at said axially outboard end by a plug (P).
5. The improved bearing assembly of Claim 1 wherein each of said inner race radially-extending flanges (2A) includes an outer circumferential surface (8) in contact with said seals (4).
6. The improved bearing assembly of Claim 1 further including a central spacer (2B) disposed between said stationary inner races (2), said central spacer (2B) having one or more lubricant delivery passages (9) for delivery of a flow of fresh lubricant to a central portion (16) of said bearing chamber axially between said rows of rolling elements (RE), and
wherein each said lubrication passage (12) is configured to discharge used lubricant accumulating axially outboard from said rows of rolling elements within said outer chamber (17) of the bearing cavity through said stationary inner race (2), said used lubricant delivered to said outer portion (17) of the bearing chamber from said central portion (16) of the bearing chamber by a pumping action of said rolling elements (RE) during bearing operation.
7. The improved bearing assembly of Claim 6 wherein a plurality of lubrication passages (12) are disposed through each inner race to provide a sufficient area and volume for a selected rate of used lubricant discharge from the bearing cavity portions (16, 17).
8. The improved bearing assembly of Claim 1 further including a central spacer (2B) disposed between said stationary inner races (2), said central spacer (2B) further including one or more lubricant purge ports (19) for discharge of used lubricant from a central portion (16) of the bearing chamber, axially between said rows of rolling elements (RE), and
wherein each said lubrication passage (12) is configured for delivery of a flow of fresh lubricant to an outer portion (17) of the bearing chamber, axially outboard from said rows of rolling elements (RE), said flow of fresh lubricant having sufficient volume to push said fresh lubricant around said rolling elements (RE) and into said central portion (16) of the bearing chamber.
9. The improved bearing assembly of Claim 1 wherein said seal (4) has a minimized section height in the radial direction.
10. The improved bearing assembly of Claim 1 wherein said seal carrier has a minimized radial thickness.
11. An axially compact bearing assembly (A), comprising: an inner race (2);
an outer race (3), said inner race (2) and said outer race (3) rotating relative to each other;
a set of rolling elements (RE) disposed with a bearing chamber between the inner race (2) and the outer race (3);
a pair of seals (4) axially enclosing the bearing chamber at opposite axial ends, each seal (4) supported on a seal carrier (5) secured to one of the races; and
at least one lubrication passage (12) disposed in the inner race, said lubrication passage in fluid communication with an opening within the bearing chamber at an axially-inward face (14) of an outboard flange (2A) of the inner race (2).
12. The axially compact bearing assembly (A) of Claim 1 1 wherein said lubrication passage (12) is configured to deliver a flow of lubricant to an outer portion (17) of said bearing chamber adjacent to said set of rolling elements (RE).
13. The axially compact bearing assembly (A) of Claim 1 1 wherein said lubrication passage (12) is configured to discharge a flow of lubricant from said outer portion (12) of said bearing chamber.
PCT/US2012/030800 2011-03-28 2012-03-28 Bearing lubrication passage Ceased WO2012135254A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161468260P 2011-03-28 2011-03-28
US61/468,260 2011-03-28

Publications (1)

Publication Number Publication Date
WO2012135254A1 true WO2012135254A1 (en) 2012-10-04

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762151A (en) * 2016-11-29 2017-05-31 沈阳黎明航空发动机(集团)有限责任公司 A kind of aeroplane engine main bearing inner ring integral structure
EP3173642A1 (en) * 2015-11-27 2017-05-31 ALSTOM Renewables Technologies Wind B.V. Wind turbine generator with bearing system and seal
DE102017106957A1 (en) * 2017-03-31 2018-10-04 Schaeffler Technologies AG & Co. KG roller bearing
DE102017109777A1 (en) * 2017-05-08 2018-11-08 Schaeffler Technologies AG & Co. KG Sealed large roller bearing
US20200025252A1 (en) * 2017-03-31 2020-01-23 Schaeffler Technologies AG & Co. KG Sealed roller bearing

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US3497277A (en) * 1968-09-03 1970-02-24 Gen Motors Corp Bearing lubrication
JPH0988986A (en) * 1995-09-27 1997-03-31 Ntn Corp Lubricative cooling method and device of angular contact ball bearing
JP2003343586A (en) * 2002-05-29 2003-12-03 Nsk Ltd Sealed rolling bearing
JP2003343587A (en) * 2002-05-31 2003-12-03 Nsk Ltd Rolling bearing
EP1712806A2 (en) * 2005-04-15 2006-10-18 Snecma Assembly arrangement between an inner bearing ring and a trunnion, bearing ring and trunnion adapted to the arrangement, and a turbo machine equipped with them

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US3497277A (en) * 1968-09-03 1970-02-24 Gen Motors Corp Bearing lubrication
JPH0988986A (en) * 1995-09-27 1997-03-31 Ntn Corp Lubricative cooling method and device of angular contact ball bearing
JP2003343586A (en) * 2002-05-29 2003-12-03 Nsk Ltd Sealed rolling bearing
JP2003343587A (en) * 2002-05-31 2003-12-03 Nsk Ltd Rolling bearing
EP1712806A2 (en) * 2005-04-15 2006-10-18 Snecma Assembly arrangement between an inner bearing ring and a trunnion, bearing ring and trunnion adapted to the arrangement, and a turbo machine equipped with them

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3173642A1 (en) * 2015-11-27 2017-05-31 ALSTOM Renewables Technologies Wind B.V. Wind turbine generator with bearing system and seal
CN106762151A (en) * 2016-11-29 2017-05-31 沈阳黎明航空发动机(集团)有限责任公司 A kind of aeroplane engine main bearing inner ring integral structure
DE102017106957A1 (en) * 2017-03-31 2018-10-04 Schaeffler Technologies AG & Co. KG roller bearing
US20200025252A1 (en) * 2017-03-31 2020-01-23 Schaeffler Technologies AG & Co. KG Sealed roller bearing
US10890215B2 (en) * 2017-03-31 2021-01-12 Schaeffler Technologies AG & Co. KG Sealed roller bearing
DE102017109777A1 (en) * 2017-05-08 2018-11-08 Schaeffler Technologies AG & Co. KG Sealed large roller bearing

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