US20160091019A1 - Bearing ring - Google Patents

Bearing ring Download PDF

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Publication number
US20160091019A1
US20160091019A1 US14/869,233 US201514869233A US2016091019A1 US 20160091019 A1 US20160091019 A1 US 20160091019A1 US 201514869233 A US201514869233 A US 201514869233A US 2016091019 A1 US2016091019 A1 US 2016091019A1
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US
United States
Prior art keywords
bearing ring
edge
bearing
rolling
mounting
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.)
Abandoned
Application number
US14/869,233
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English (en)
Inventor
Padelis Katsaros
Volker Wendt
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.)
SKF AB
Original Assignee
SKF AB
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 SKF AB filed Critical SKF AB
Assigned to AKTIEBOLAGET SKF reassignment AKTIEBOLAGET SKF ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KATSAROS, PADELIS, WENDT, VOLKER
Publication of US20160091019A1 publication Critical patent/US20160091019A1/en
Priority to US15/715,861 priority Critical patent/US10247236B2/en
Abandoned legal-status Critical Current

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    • 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
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • 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
    • F16C19/364—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips

Definitions

  • the present disclosure relates to a bearing ring for a rolling-element bearing, in particular for a tapered roller bearing, as well as a rolling element with line contact for a rolling-element bearing, and a rolling-element bearing including such a bearing ring and/or such a rolling element.
  • Rolling-element bearings with line contact are bearings in which the rolling elements contact running surfaces of the bearing rings along a line.
  • off-center loads can produce a skewing/misalignment at mutually opposing ends of the rolling elements.
  • This skewing/misalignment can lead to very high bearing loads, sometime referred to as edge stresses. It has therefore been proposed in the prior art to provide bearing components, in particular bearing rings and rolling elements, with a convex profile that allows a load to be distributed relatively uniformly over the rolling elements even in the case of an uneven load or skewing.
  • the convex profile is usually formed on the running surfaces and/or the rolling elements by grinding and/or honing the surfaces after turning and hardening the bearing components.
  • the profiles ensure that loads are relatively uniformly distributed over the rolling elements even in the case of uneven loading or skewing.
  • a disadvantage with using convex profiles is that the profiling operation must be performed with high precision. This is only possible to a limited extent over the course of a long production period. This is because, for example, the grinding and honing stones used to form the profile may wear over the course of production, and this can result in an increasing deviation of the profile from the target. In some cases, this deviation can even increase the edge stress problem. In addition, the processing/machining of the bearing components is very cost-intensive.
  • a further disadvantage of using profiled elements is that, because of the profiling, the rolling elements no longer abut on the running surfaces over their entire lengths. This in turn increases the pressure load on the rolling elements and thus reduces the load capacity of the rolling-element bearing.
  • An aspect of the present disclosure is therefore to provide a rolling-element bearing that is simple to produce, that has a long service life, and that is resistant to problems that can be caused by skew or uneven or offset loads.
  • a bearing ring for a rolling-element bearing in particular for a tapered roller bearing, is provided.
  • the bearing ring includes a running surface for a rolling element and a mounting surface extending essentially axially, and the bearing ring is configured to connect to a to-be-supported element such that they rotate together.
  • the bearing ring includes a first and a second edge surface extending essentially radially, which edge surfaces axially delimit the bearing ring.
  • the bearing ring includes on at least one of its edge surfaces an edge which is designed to be flexible under pressure load.
  • edge stress can be counteracted without the need to provide the running surface of the bearing ring and/or of the rolling elements with a profile.
  • the flexible edge can yield under pressure load so that the edge stresses can be reduced.
  • the flexible edge it is also still possible to provide a profiling of one or more of the bearing components.
  • the flexible edge is formed over at least one recess formed in the first and/or second edge surface and/or in the mounting surface. Since bearing rings are usually manufactured from steel or metal and are formed solid, the inventively designed recess makes it possible to form a flexible edge via a reduction in material in the edge region.
  • the flexible edge can be adapted in terms of its material strength to the expected loads, and above all with respect to its flexibility. If now due to skewing of the bearing components a pressure is exerted on this edge by a rolling element, then due to the recess the edge can flex away from the rolling element and thereby mitigate the edge stress that would otherwise arise
  • the recess is groove-shaped.
  • Such a groove can be turned in the bearing ring or even formed during forging. Unlike a profiling, creating the groove does not require high-precision work and it is therefore easier and more cost-effective to manufacture a bearing ring with a groove than a profiled bearing ring.
  • the recess can be designed larger, so that the recess extends up to the mounting surface, and so that the running surface has a greater axial extension than the mounting surface.
  • a recess can be produced, for example, by a corresponding shaping during forging or turning. This design is also easy to produce and therefore cost-effective to form.
  • the mounting surface can include a first mounting-surface region and a second mounting-surface region radially offset to the first mounting-surface region, which second mounting-surface region merges into the edge region and forms the flexible edge.
  • a gap is thus formed between the mounting-surface region of the bearing ring and an element receiving the bearing ring, which gap makes possible a bending- or springing-in for the flexible edge.
  • the mounting ring Since in particular in tapered roller bearings the mounting ring has only a very small edge surface on its larger diameter, which edge surface merges directly into the mounting surface, and the mounting surface directly contacts the to-be-supported element, it is advantageous to integrate the mounting surface into the edge design and for a space to be provided over the radially offset mounting surface region into which the flexible edge can bend or spring in.
  • the first and/or second edge surface includes a first edge-surface region and a second edge-surface region axially displaced with respect to the first edge-surface region, wherein the first or the second edge-surface region forms the flexible edge.
  • the space required for the flexible design of the edge can be provided even if the bearing ring directly contacts an axially-adjacently-disposed element. This is particularly advantageous if the bearing ring is axially secured by a securing element, which in particular can extend beyond the entire radial extension of the bearing ring.
  • the above-mentioned inventive design of the bearing rings is particularly advantageous in outer rings, since a profiling of the inwardly facing running surfaces can reduce their ability to guide the rolling elements.
  • the required geometries for the flexible edge can be formed in a simple and rapid manner, for example, by turning the outer ring.
  • this shape can also be implemented without problems on the small diameter of the raceway.
  • a guide flange that is convex towards the raceway can be provided on the outer diameter with its adjacent guide flange in order to provide a good rolling guiding and also allow a raceway region to deform.
  • a rolling element itself can also contribute to a reduction of the edge stress.
  • a further aspect of the present disclosure relates to a rolling element with line contact for a rolling-element bearing, in particular a tapered roller, wherein the rolling element has a circumferential surface that is designed to contact a running surface along a line.
  • the rolling elements include two essentially radial boundary surfaces.
  • the circumferential surface is inventively designed such that an edge region designed to be flexible is provided at least in the region of one of the radial boundary surfaces. This can be realized, for example, via a material reduction in the edge region, for example, in the form of a hollowing-out.
  • this flexible end region makes it possible that in particular in the event of skewings, wherein high loads arise on the edges of the rolling-element bearing, either the edges of the bearing rings supporting the rolling elements and/or just the edges of the rolling elements can flex. As a result, a cushioned (spring-absorbed) tipping of the rolling elements can be made possible, whereby the edge-stress peaks can be decreased or reduced.
  • a further aspect of the present invention relates to a rolling-element bearing including a first and a second bearing ring that are configured to be rotatable with respect to each other, and between which at least one rolling element is received.
  • the first and/or the second bearing ring and/or the rolling element is configured with a flexible edge as described above. In this way a rolling-element bearing can be provided that has reduced edge stress and whose service life is thereby increased.
  • a bearing ring for a rolling-element bearing that includes a mounting surface having a first length, and a running surface configured to support a rolling element that has a second length.
  • the running surface has first and second axially spaced end portions, and at least one of the first and second axially spaced end portions comprises a cantilever.
  • the word “cantilever” refers to the appearance of the end portions of the running surface in section, as illustrated in FIGS. 1 and 2 , for example.
  • the “cantilever” actually comprises a continuous ring extending around the axis of rotation of the bearing, but the word cantilever is intended to convey the sense of a portion that projects in the manner of a conventional cantilever.
  • FIG. 1 is a schematic sectional side elevational view of a first preferred exemplary embodiment of a bearing ring according to the present disclosure.
  • FIG. 2 is a schematic sectional side elevational view of a second preferred exemplary embodiment of a bearing ring according to the present disclosure.
  • FIG. 3 is a schematic sectional side elevational view of a third preferred exemplary embodiment of a bearing ring according to the present disclosure.
  • FIG. 4 is a sectional side elevational view of a first tapered rolling element according to an exemplary embodiment.
  • FIG. 5 is a sectional side elevational view of a second tapered rolling element according to an exemplary embodiment.
  • FIG. 1 schematically shows a sectional view through a part of a rolling-element bearing assembly 100 .
  • the rolling-element bearing assembly 100 includes a rolling-element bearing 1 , in this case a tapered roller bearing that has a bearing inner ring (not illustrated), a bearing outer ring 2 , and a rolling element 4 .
  • the rolling-element bearing 1 or more specifically the outer ring 2 , is press-fit in a housing 6 .
  • the bearing outer ring 2 has a running surface 8 along which the rolling element 4 runs. Furthermore, the outer ring 2 includes an outer surface 10 that contacts the housing 6 , and the outer ring 2 is press-fit in the housing 6 .
  • the bearing outer ring 2 is laterally bounded by edge surfaces 12 , 14 , which axially delimit the bearing ring 2 .
  • the outer surface 10 forms a mounting surface for mounting the outer ring 2 in the housing 6 .
  • FIG. 1 further shows that the bearing outer ring 2 includes flexible edges 16 , 18 that can move elastically towards housing 6 if forces are applied over the rolling element 4 , especially forces that are not centered over the rolling element 4 . This helps reduce or prevent edge stresses between the rolling element 4 and the bearing outer ring 2 , even when the bearing ring 2 and/or the rolling element 4 lacks a convex profiling.
  • the edge surfaces 12 , 14 include a first edge-surface region 12 - 1 , 14 - 1 and a second edge-surface region 12 - 2 , 14 - 2 .
  • the second edge-surface regions 12 - 2 , 14 - 2 are offset axially inward from the edge surfaces 12 , 14 so that the first edge-surface regions 12 - 1 , 14 - 1 form the flexible edges 16 , 18 .
  • a greater or lesser spring action can be achieved depending on the thickness d of the edges 16 , 18 thus provided.
  • FIG. 1 shows that in this exemplary embodiment the axial length L 1 of the running surface 8 is larger than the axial length L 2 of the outer surface 10 of the bearing ring 2 .
  • Profiling the running surface 8 is disadvantageous, especially when the running surface 8 is part of an outer ring, because the rolling elements are not optimally guided. Therefore, by using the disclosed outer ring configuration having flexible edges 16 , 18 , edge stress between the bearing ring 2 and the rolling element 4 can be reduced or eliminated even when skewing or offset loading occurs.
  • FIG. 2 schematically shows a sectional view through a part of a rolling-element bearing assembly 100 that includes a tapered rolling-element bearing 1 having an inner ring 3 , an outer ring (not illustrated) and the rolling element 4 .
  • the rolling-element bearing 1 more specifically the inner ring 3 , is press fit in the housing 6 .
  • the bearing inner ring 3 has a running surface 8 along which the rolling element 4 runs. Furthermore, the inner ring 3 includes an inner surface 10 that contacts the housing 6 or other support (not illustrated). The bearing inner ring 3 is laterally bounded by edge surfaces 12 , 14 , that axially delimit the bearing ring 3 . The inner surface 10 forms a mounting surface for mounting the inner ring 6 on the housing 6 or other support.
  • flexible edges 16 , 18 are formed on the bearing inner ring 3 and can move elastically towards the housing 6 in response to pressure or force being applied over the rolling element 4 , and this movement reduces edge stresses between the rolling element 4 and the bearing inner ring 3 .
  • the edge surfaces 12 , 14 include a first edge surface region 12 - 1 , 14 - 1 and a second edge surface region 12 - 2 , 14 - 2 .
  • the second edge surface regions 12 - 2 , 14 - 2 are offset axially inward from the edge surfaces 12 , 14 , so that the first edge surface regions 12 - 1 , 14 - 1 form the flexible edges 16 , 18 .
  • the rolling elements 4 and either the inner or outer bearing ring is profiled. It is also comprised in the scope of the disclosure that the outer ring 2 has a profiling, and only the inner ring includes flexible edges as described above. Alternatively or in addition to the embodiments depicted in FIGS. 1 and 2 , the rolling elements 4 themselves can also be flexible in an edge region 20 , 22 , so that a reduction of the edge stress is also thereby possible. For this purpose, for example, the rolling elements 4 can be hollowed-out in at least one of the edge regions 20 , 22 .
  • FIG. 4 shows how the concept of the present disclosure can be applied to a rolling element 40 of a rolling element bearing instead of or in addition to the bearing cages of a rolling element bearing.
  • the rolling element 40 is a rolling element with linear contact for a tapered rolling-element bearing.
  • the rolling element 40 includes a circumferential surface 42 configured to contact a running surface (not illustrated) along a line, and two radial boundary surfaces 44 .
  • the circumferential surface 42 has at least one flexible, cantilevered, edge 46 , and these edges 46 provide flexibility in response to skew forces applied to a bearing including such rolling elements.
  • FIG. 5 shows another exemplary embodiment of a rolling element 40 of a tapered rolling element bearing that includes cantilevers 46 , in this case formed by grooves 48 in the boundary surfaces 44 .
  • a securing element 24 may be provided for axially securing the outer ring 2 or the inner ring 3 .
  • the securing element 24 preferably abuts directly on the edge surface 14 , in the depicted exemplary embodiment, in particular on the set-back edge surface region 14 - 2 , in order to limit an axial movement of the bearing ring 2 ; 3 .
  • the securing element 24 can be configured as a snap ring or locking ring; however, it is also possible to configure the securing element 24 as an integral component of the housing 6 . However, in order to ensure a sufficient flexibility of the edge 18 , the securing element 24 should be disposed at least at a sufficient distance from the edge 18 .
  • FIG. 3 shows a further advantageous exemplary embodiment of a bearing ring.
  • the housing 6 is formed integrally with a securing element 24 , and the securing element 24 extends beyond the radial length of the bearing ring 2 .
  • Such housing designs provide a particularly secure holding of the bearing ring 2 .
  • the edge surface 14 is formed such that the second edge region 14 - 2 is not offset axially inward, but the first edge region 14 - 1 is offset axially inward, so that a gap 26 is produced between the edge 18 or the first edge region 14 - 1 and the securing element 24 .
  • a flexibility groove 28 is further provided, and this makes possible an elastic design of the edge 18 .
  • FIG. 3 further shows that another flexibility groove 30 may be formed in the outer surface 10 .
  • the edge 16 is not configured over the edge region 12 as in FIG. 1 , since the edge surface 12 is already very narrow, but rather the outer surface 10 includes a first outer-surface region 10 - 1 and a second outer-surface region 10 - 2 , and the second outer-surface region 10 - 2 is offset radially inward so that a gap 32 remains between housing 6 and second outer-surface region 10 - 2 .
  • the second outer-surface region 10 - 2 merges directly into the edge region 12 , and together with the edge region 12 forms the flexible edge 16 .
  • the gap 32 and the flexibility groove 30 provide a flexibility of the edge 16 in the event of pressure load.
  • a rolling-element bearing can be provided that has reduced edge stress and thus a longer service life.
  • the disclosed rolling-element bearing simultaneously enables contact of the rolling element on the running surface of the bearing rings to be maximized, so that a pressure load on the rolling element is less than in the case of conventional rolling element bearings. Since according to the disclosure the edges are designed to be flexible, a uniform loading can nevertheless be achieved even in the region of the edges in the event of skewing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
US14/869,233 2014-09-29 2015-09-29 Bearing ring Abandoned US20160091019A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US15/715,861 US10247236B2 (en) 2014-09-29 2017-09-26 Bearing ring

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014219705.8 2014-09-29
DE102014219705.8A DE102014219705B4 (de) 2014-09-29 2014-09-29 Lagerring

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US15/715,861 Continuation US10247236B2 (en) 2014-09-29 2017-09-26 Bearing ring

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US20160091019A1 true US20160091019A1 (en) 2016-03-31

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US14/869,233 Abandoned US20160091019A1 (en) 2014-09-29 2015-09-29 Bearing ring
US15/715,861 Active US10247236B2 (en) 2014-09-29 2017-09-26 Bearing ring

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Application Number Title Priority Date Filing Date
US15/715,861 Active US10247236B2 (en) 2014-09-29 2017-09-26 Bearing ring

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US (2) US20160091019A1 (de)
CN (1) CN105465182B (de)
DE (1) DE102014219705B4 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10228024B2 (en) 2017-01-10 2019-03-12 General Electric Company Reduced-weight bearing pins and methods of manufacturing such bearing pins
US10247298B2 (en) 2017-01-10 2019-04-02 General Electric Company Resilient bearing pin and gear assemblies including resilient bearing pins

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019007309A1 (de) 2018-11-23 2020-05-28 Sew-Eurodrive Gmbh & Co Kg Lagersystem mit einem Lager und Getriebe mit einem Lagersystem

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FR3017430A1 (fr) * 2014-02-07 2015-08-14 Ntn Snr Roulements Bague de roulement, et roulement, assemblage et procede d'assemblage associes a cette bague

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Publication number Priority date Publication date Assignee Title
US7537391B2 (en) * 2004-02-03 2009-05-26 Hansen Transmissions International, Naamloze Vennootschap Roller bearing
FR3017430A1 (fr) * 2014-02-07 2015-08-14 Ntn Snr Roulements Bague de roulement, et roulement, assemblage et procede d'assemblage associes a cette bague

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10228024B2 (en) 2017-01-10 2019-03-12 General Electric Company Reduced-weight bearing pins and methods of manufacturing such bearing pins
US10247298B2 (en) 2017-01-10 2019-04-02 General Electric Company Resilient bearing pin and gear assemblies including resilient bearing pins

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Publication number Publication date
DE102014219705A1 (de) 2016-03-31
CN105465182A (zh) 2016-04-06
US20180017104A1 (en) 2018-01-18
CN105465182B (zh) 2020-10-30
DE102014219705B4 (de) 2023-04-27
US10247236B2 (en) 2019-04-02

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