US20160238068A1 - Combination spherical and laminated bearing - Google Patents

Combination spherical and laminated bearing Download PDF

Info

Publication number
US20160238068A1
US20160238068A1 US14/645,467 US201514645467A US2016238068A1 US 20160238068 A1 US20160238068 A1 US 20160238068A1 US 201514645467 A US201514645467 A US 201514645467A US 2016238068 A1 US2016238068 A1 US 2016238068A1
Authority
US
United States
Prior art keywords
bearing
laminated
bearing portion
spherical
recited
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
US14/645,467
Other languages
English (en)
Inventor
Anthony Carl Bohm
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
Priority to US14/645,467 priority Critical patent/US20160238068A1/en
Assigned to AKTIEBOLAGET SKF reassignment AKTIEBOLAGET SKF ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BOHM, ANTHONY CARL
Publication of US20160238068A1 publication Critical patent/US20160238068A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02Sliding-contact bearings
    • F16C23/04Sliding-contact bearings self-adjusting
    • F16C23/043Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02Sliding-contact bearings
    • F16C23/04Sliding-contact bearings self-adjusting
    • F16C23/043Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
    • F16C23/045Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for radial load mainly, e.g. radial spherical plain bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06Ball or roller bearings
    • F16C23/08Ball or roller bearings self-adjusting
    • F16C23/082Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/084Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/063Sliding contact bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02Parts of sliding-contact bearings
    • F16C33/04Brasses; Bushes; Linings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02Parts of sliding-contact bearings
    • F16C33/04Brasses; Bushes; Linings
    • F16C33/06Sliding surface mainly made of metal
    • F16C33/12Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
    • F16C33/122Multilayer structures of sleeves, washers or liners
    • F16C33/125Details of bearing layers, i.e. the lining
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00Springs
    • F16F1/36Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/3842Method of assembly, production or treatment; Mounting thereof
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00Springs
    • F16F1/36Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/393Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type with spherical or conical sleeves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00Pivots; Pivotal connections
    • F16C11/04Pivotal connections
    • F16C11/06Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0614Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part of the joint being open on two sides
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00Articles relating to transporting
    • F16C2326/43Aeroplanes; Helicopters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00Springs
    • F16F1/36Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/40Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers consisting of a stack of similar elements separated by non-elastic intermediate layers

Definitions

  • the present disclosure is directed to a bearing having a first portion configured to respond to frequent but small relative movements between inner and outer portions of the bearing and a second portion configured to respond to large, infrequent, relative movements between the inner and outer portions, and, more specifically, to a bearing having an laminated bearing portion configured to respond to frequent but small relative movements between inner and outer portions of the bearing and a spherical bearing portion configured to respond to larger, infrequent, relative movements between the inner and outer portions.
  • Laminated bearings may be used to accommodate relative movement between inner and outer components, which movement may occur along and/or about any one of three mutually perpendicular axes.
  • Such bearings generally comprise a plurality of alternating, generally tubular elastomeric laminae and metallic laminae nested coaxially about a central axis.
  • One common application of such bearings is at the ends of the pitch arms of rotary wing aircraft, which pitch arms connected between a rotary swash plate and a pitch horn of a blade grip that secures one of the blades.
  • Such bearings are used in other environments as well.
  • the degree of movement allowed by a laminated bearing is determined in part by the number of elastomeric lamellae used as well as their properties.
  • each of the elastomeric lamellae is formed from an elastomeric material having an elastic limit.
  • Each lamina can therefor be subjected to forces of up to a predetermined amount and still return elastically to its original shape and size. Forces greater than the elastic limit of the lamina will permanently deform the lamina.
  • the plurality of the lamella in the laminated bearing thus allow the bearing to withstand a given level of strain without being permanently deformed.
  • the entire bearing may therefore be described as having its own elastic limit, that is, a maximum force or strain to which the bearing can be subjected without permanently damaging the bearing.
  • the maximum strain level to which a bearing can be subjected without unnecessarily shortening its operating life will depend on many factors, including the materials used for the elastomeric and metallic lamellae, the number of lamellae provided, the configuration of the bearing, and the types of forces to which the bearing is subjected, e.g., rotational, radial, axial, tilting, etc. However, it may generally be assumed that subjecting a bearing to strains less than 50% of the elastic limit of the bearing is desirable.
  • a first aspect of which comprises a bearing that includes a laminated bearing portion and a spherical bearing portion, and in which the spherical bearing portion is disposed within the laminated bearing portion or the laminated bearing portion is disposed within the spherical bearing portion.
  • Another aspect of the disclosure comprises a method of operating a bearing which bearing includes a laminated bearing portion and a spherical bearing portion, the spherical bearing portion being disposed within the laminated bearing portion or the laminated bearing portion being disposed within the spherical bearing portion.
  • the spherical bearing portion comprises a generally annular outer race having a concave inner circumferential surface, the inner surface being partially spherical and defining a central opening, and a ball disposed within the outer race central opening and having a convex, partially spherical, outer surface in contact with the inner surface of the outer race portion.
  • the ball and the outer race are configured such that the ball is locked in the outer race and such that a given break-out force is required to move the ball relative to the outer race.
  • the method includes repeatedly applying first forces to the bearing to deform the laminated bearing portion without exceeding the given break-out force of the spherical bearing.
  • a further aspect of the disclosure comprises a bearing having an inner bore, an outer housing, and means between the inner bore and outer housing for repeatedly elastically accommodating relative movement between the inner bore and the outer housing of up to a first magnitude and for repeatedly slidably accommodating relative movement between the inner bore and the outer housing of a second magnitude greater than the first magnitude.
  • FIG. 1 is a sectional elevational view of a bearing according to an embodiment of the present disclosure.
  • FIG. 2 is a perspective view of the bearing section of FIG. 1 .
  • FIG. 3 is a graph showing a relationship between a moment and an amount of bearing rotation.
  • FIG. 4 is a sectional perspective view of a bearing according to another embodiment of the disclosure.
  • FIGS. 1 and 2 show a bearing 10 according to an embodiment of the present disclosure.
  • the bearing 10 of this embodiment is symmetric about a central axis of rotation 12 and has a circular cross section perpendicular to the axis of rotation 12 .
  • the terms “radial” and “axial” may therefore be used hereinafter to describe the relative locations of elements of the bearing.
  • the bearing 10 includes an outer member 14 having a radially outer surface 16 and a radially inner surface 18 and having a first thickness in the axial direction.
  • the outer surface 16 is convex and the inner surface 18 is concave, and, preferably, the inner surface 18 (or at least part of the inner surface 18 ) is a spherical surface, that is, a surface all points of which are a constant distance from a center point.
  • the bearing also includes an inner member 20 having a radially outer surface 22 and a radially inner surface 24 and having a second thickness in the axial direction.
  • the radially outer surface 22 is convex and preferably spherical, and the second axial thickness of the inner member 20 is less than the first axial thickness of the outer member 14 .
  • the outer member 14 and the inner member 20 are coaxial, and the inner member 20 is axially centered with respect to the outer member 14 .
  • a first sheet or lamina of elastomeric material 26 a is bonded to the inner surface 18 of the outer member 14
  • a thirteenth sheet or lamina of elastomeric material 26 m is bonded to the outer surface 22 of the inner member 20 .
  • Eleven central lamellae 26 b - 26 l are disposed between the first lamina 26 a and the thirteenth lamina 26 m in this embodiment, and one metallic shim or metallic lamina 28 is disposed between each adjacent pair of elastomeric laminae 26 a - 26 m .
  • a total of twelve metallic shims 28 a - 28 l are present in this embodiment, with a first metallic shim 28 a disposed between the first elastomeric lamina 26 a and the second elastomeric lamina 26 b .
  • Different numbers of elastomeric laminae and metallic shims can be used without exceeding the scope of this disclosure, and this number will be based on the forces that must be accommodated by the laminated bearing.
  • the axial lengths of the elastomeric lamellae 26 a - 26 m decrease in the direction from the first elastomeric lamella 26 a to the thirteenth elastomeric lamella 26 m
  • the axial lengths of the metallic lamellae 28 a - 28 l decrease from the first metallic lamella 28 a to the twelfth metallic lamella 28 l as well so that the axial length of the bearing, defined by edges of the nested elastomeric lamellae 26 and the metallic lamellae 28 decreases from the outer member 14 to the inner member 20 .
  • the bearing 10 further comprises a shell 30 mounted inside the inner member 20 , the shell 30 having an outer side 32 connected to the radially inner surface 24 of the inner member 20 and an inner surface 34 that is concave and preferably spherical.
  • the inner surface 34 of the shell 30 forms a race for a spherical bearing ball 36
  • the bearing ball 36 has a spherical outer surface 38 in contact with the inner surface 34 of the shell 30 and a central bore 40 coaxial with the shell 30 .
  • the laminated bearing is configured to allow small amounts of relative axial, radial, rotational and tilting movement between the outer member 14 and the inner member 20 , and, in particular, is configured to accommodate small changes that are frequent and/or rapid.
  • the shell 30 and the spherical ball 36 together form a spherical bearing 44 .
  • the bearing 10 may therefore be described as a spherical bearing 44 mounted inside a laminated bearing 42 .
  • each of the elastomeric lamellae 26 that form the laminated bearing 42 has various properties.
  • each of the elastomeric lamellae 26 is formed from the same material, and the elastomeric lamellae 26 thus have similar or substantially identical properties.
  • various ones of the elastomeric lamellae 26 could be formed of different materials and have different properties if desired.
  • One of the properties of the elastomeric lamellae is the elastic limit of the material from which they are formed. That is, each of the elastic lamellae can withstand a given stress or force per unit area without being permanently deformed. Greater amounts of stress or force, on the other hand, will change the structure of the lamellae in such a manner that the lamella will not return to its original shape or form when the stress or force is removed.
  • Conventional laminated bearings are designed so that the elastic limit of the elastomeric layers of the bearing will not be exceeded during use. That is, a conventional bearing must be designed to withstand the greatest forces to which it is likely to be subjected in a particular environment. These extreme forces may rarely occur, but if the bearing is not designed to accommodate them, the bearing will be permanently damaged any time they are encountered. Conventional bearings therefore generally operate over a range of forces that are only a faction of the elastic limit of the elastomeric materials contained therein in order to provide a margin of error and to accommodate occasional extreme forces.
  • Laminated bearings are well-suited for use in environments where small changes occur in the relative positions of the inner and outer portions of the bearing, especially when these changes are rapid and/or frequent.
  • conventional laminated bearings are not able to accommodate relatively large changes in the relative positions of the inner and outer portions.
  • Spherical bearings made from metal or other materials, on the other hand, can withstand significant forces and accommodate larger angular and rotational changes between an inner member or ball and an outer member or race.
  • the frictional contact between the ball and the race may lead to rapid wear, especially when such bearings are used to accommodate frequent small, and in particular, rapid changes in the relative positions of the elements supported by the bearing.
  • the present inventor has addressed these issues by mounting a spherical bearing 44 inside a laminated bearing 42 to provide the laminated bearing 42 with some of the beneficial qualities of spherical bearings.
  • the ball 36 of the spherical bearing 44 is fitted or swaged in the shell 30 so that a certain minimum level of force is required to cause the ball 36 to move in the race formed by the inner surface 34 .
  • This force may sometimes be referred to as a “break-out” force and may be applied to the ball 36 by a shaft (not illustrated) running through the axial bore 40 of the ball 36 .
  • Conventional spherical bearings are generally designed to have a low break-out force to allow a smooth transition to dynamic motion. In the present embodiment, the break-out force is significantly greater than normal.
  • the phrase “dynamic friction force” will be used herein to refer to the level of force at which the ball 36 relocks in the shell 30 .
  • the spherical bearing 44 thus does not begin to operate until an applied force exceeds the break-out force, and will continue to operate until the applied force falls below the dynamic friction force. At that point, the spherical bearing 44 relocks in the shell 30 , and the laminated bearing 42 again begins to operate.
  • the dynamic friction force may be, for example, 80% or more of the break-out force.
  • the break-out force and dynamic friction forces are selected such that the bearing 10 will function with the spherical bearing 42 locked under most operating conditions. Under such conditions, the spherical bearing 44 behaves essentially as part of the inner member 20 of the laminated bearing and merely transmits forces from the shaft in the central bore 40 to the elastomeric lamellae 26 a - 26 m . Under these operating conditions, the laminated bearing 42 will absorb substantially all forces applied to the bearing. However, when forces are applied to the bearing 10 greater than the spherical bearing break-out force, the ball 36 will shift in the shell 30 .
  • the spherical bearing 42 will thereafter move and accommodate changes in the orientation of the shaft and the outer member 14 until the force applied to the bearing falls below the dynamic friction force and the ball 36 once again locks in the shell 36 .
  • the laminated bearing 42 will once again accommodate all forces applied to the bearing 10 .
  • it is expected that the relative movement allowed by the ball 36 breaking free of the shell 36 will quickly relieve stress on the bearing 10 so that the forces experienced by the bearing 10 rapidly fall below the dynamic friction force and allow the laminated bearing 42 to once again become the primary mechanism for accommodating changes in the relative positions of the inner and outer parts of the bearing 10 .
  • the break-out force may be exceeded when the rotational or angular movement between the shaft and the outer member 14 is greater than can be accommodated by the laminated bearing 42 , that is, at the point that the laminated bearing 42 has been stressed to a predetermined maximum amount.
  • the break-out force will then be exceeded, and the ball 36 will move in the shell 30 to prevent any further increase of force on the laminated bearing 42 .
  • sudden, large forces may exceed the break-out force and release the ball 36 from the shell 30 , thereby also protecting the laminated bearing 42 from potentially damaging levels of stress.
  • the spherical bearing 44 operates infrequently and thus wears at an acceptably slow rate.
  • FIG. 3 graphically illustrates this transition between the operation of the laminated bearing 42 and operation of the spherical bearing 44 .
  • the break-out force is generally set, by appropriate swaging of the ball 36 and the shell 30 , to be a fraction of the elastic limit of the materials from which the lamellae 26 a - 26 m are formed.
  • the dynamic friction force is determined largely by the materials from which the ball 36 and shell 30 are formed and the materials with which they are coated.
  • suitable low-friction materials such as polytetrafluoroethylene (PTFE)
  • PTFE polytetrafluoroethylene
  • the break-out force must not exceed the elastic limit of the elastomeric lamellae 26 a - 26 m in the laminated bearing 42 , and thus may be set to be from about e.g., 5% to about 75% of the elastic limit of the lamellae, for example, to 10%, 20%, 30%, 40% or 50% of the elastic limit.
  • the operating life of a laminated bearing can be determined based on the number and magnitude of oscillations to which it is subjected. Laminated bearings will last longer when they are not subjected to forces that approach the elastic limit of their lamellae. Therefore, laminated bearings are generally configured to withstand forces of up to a given amount. If greater forces need to be accommodated, a larger laminated bearing, that is, one having larger lamellae and/or a greater number of lamellae should be used.
  • the bearing may have an intended operating life of a certain number of cycles or oscillations as long as the oscillations are below a certain size.
  • the size may be expressed as an amount of force applied against the bearing or, alternately, as an amount of movement, for example, rotational or other angular movement in degrees, or radial or axial displacements in millimeters.
  • Bearing manufacturers thus may identify, for a given laminated bearing, a level of force or an angular or other amount of movement which should not be exceeded if a user wishes to maximize the life of the laminated bearing.
  • the present inventor contemplates setting the break-out force of the spherical bearing to be approximately equal to the high end of this design range of the laminated portion of the bearing so that the laminated bearing substantially always operates within its design range and such that the spherical bearing does not operate until larger forces and/or larger movements need to be accommodated.
  • FIG. 4 illustrates a bearing 50 according to a second embodiment.
  • Bearing 50 in general terms, comprises a laminated bearing 52 mounted inside a spherical bearing 54 ; that is, the locations of the laminated bearing and the spherical bearing of the first embodiment are reversed.
  • the bearing 50 includes a shell 56 having a radial outer surface 58 and a convex, preferably spherical, inner surface 60 which inner surface 60 forms a race for a spherical ball 62 .
  • the ball 62 has a central bore 64 , and the shell 56 is swaged to the ball 62 such that a certain break-out force is required to move the ball 62 relative to the shell 56 .
  • An outer member 66 of the laminated bearing 52 has a radially outer surface 68 mounted in the central bore 64 , and the outer member 66 has an spherical inner surface 70 .
  • a laminated bearing inner member 72 has a spherical outer surface 74 radially spaced from the inner surface 70 of the outer member 66 .
  • a first elastomeric lamella 76 a is mounted to the inner surface 70 of the outer member 66
  • a tenth elastomeric lamella 76 j is mounted to the outer surface 74 of the inner member and second through ninth elastomeric lamellae 76 b - 76 i are mounted between the first elastomeric lamella 76 a and the tenth elastomeric lamella 76 j .
  • Metallic shims or metallic lamellae 78 a - 78 i are mounted between each adjacent pair of elastomeric lamellae, with a first metallic lamella 78 a mounted between first elastomeric lamella 76 a and the second elastomeric lamella 76 b .
  • the inner member 72 has a central bore 80 which can be mounted to a shaft (not illustrated).
  • the bearing 50 performs in substantially the same manner and the bearing 10 discussed above. That is, the relative motion between a shaft mounted in the central bore 80 of the inner member and the shell 56 is accommodated by the laminated bearing as long as the level of force and/or amount of movement that must be accommodated is below a given level. When that level is exceeded, the break-out force that holds the ball 62 in the shell 56 is also exceeded, and further relative motion between the central bore 80 of the inner member and the shell 56 is accommodated by the movement of the ball 62 in the shell 56 .
  • Bearings such as the bearings 10 and 50 described above may be used in various environments.
  • One common use of such bearings is at the ends of the pitch arms of rotary wing aircraft, which pitch arms are connected between a rotary swash plate and a pitch horn of a blade grip that secures one of the blades.
  • small and/or frequent and/or rapid changes occur between the ends of the pitch arm and the structures to which they are mounted, and most of these motions are accommodated by the laminated bearing 42 of the bearing 10 or the laminated bearing 52 of the bearing 50 .
  • the spherical bearing 44 of the bearing 10 or the spherical bearing 54 of the bearing 50 breaks free and accommodates the motion.
  • the laminated bearing need only be sized to accommodate the most common degree of relative movement likely to be encountered in a given environment, and the spherical bearing can accommodate the less common motions without requiring the use of an oversized laminated bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Architecture (AREA)
  • Support Of The Bearing (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Automation & Control Theory (AREA)
  • Aviation & Aerospace Engineering (AREA)
US14/645,467 2015-02-12 2015-03-12 Combination spherical and laminated bearing Abandoned US20160238068A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/645,467 US20160238068A1 (en) 2015-02-12 2015-03-12 Combination spherical and laminated bearing

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562115437P 2015-02-12 2015-02-12
US14/645,467 US20160238068A1 (en) 2015-02-12 2015-03-12 Combination spherical and laminated bearing

Publications (1)

Publication Number Publication Date
US20160238068A1 true US20160238068A1 (en) 2016-08-18

Family

ID=55450980

Family Applications (2)

Application Number Title Priority Date Filing Date
US14/645,467 Abandoned US20160238068A1 (en) 2015-02-12 2015-03-12 Combination spherical and laminated bearing
US15/042,572 Active US9709089B2 (en) 2015-02-12 2016-02-12 Combination spherical and laminated bearing assembly

Family Applications After (1)

Application Number Title Priority Date Filing Date
US15/042,572 Active US9709089B2 (en) 2015-02-12 2016-02-12 Combination spherical and laminated bearing assembly

Country Status (3)

Country Link
US (2) US20160238068A1 (zh)
EP (1) EP3056749B1 (zh)
CN (1) CN106151263B (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170165520A1 (en) * 2015-12-09 2017-06-15 Ultimate Shoulder Exerciser, Inc. Exercise Device for the Shoulder
US20190144106A1 (en) * 2017-11-16 2019-05-16 Aktiebolaget Skf Combination elastomeric and ellipsoidal plain bearing
US10371200B2 (en) * 2017-12-06 2019-08-06 Aktiebolaget Skf Combination elastomeric and cylindrical plain bearing
US11105381B2 (en) * 2020-02-04 2021-08-31 Aktiebolaget Skf Rotor assembly bearing with centrifugal clutch mechanism

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3052828B1 (fr) * 2016-06-21 2018-06-08 Safran Helicopter Engines Bielle de longueur reglable pour turbomachine
US11255379B2 (en) 2016-09-22 2022-02-22 Sikorsky Aircraft Corporation Uniball bearing with compliant inner member
US10442532B2 (en) * 2016-11-18 2019-10-15 Sikorsky Aircraft Corporation Composite swashplate guide for rotorcraft control systems
EP3648904B1 (en) * 2017-07-05 2023-03-22 M-I L.L.C. Spherical elastomeric mounts
US10233992B2 (en) * 2017-07-31 2019-03-19 Aktiebolaget Skf Elastomeric bearing component with wedge-shaped shims
US11802547B2 (en) * 2017-12-08 2023-10-31 Fm Energie Gmbh & Co. Kg Bearing structure made of elastomer bearing elements which can be mounted and exchanged individually
US10584745B2 (en) 2018-02-21 2020-03-10 Lord Corporation Asymmetric bearing for riser tensioner system
US11060605B2 (en) 2018-07-09 2021-07-13 Textron Innovations Inc. Spherical mounted cylindrical roller bearing system
US11015652B2 (en) 2019-01-21 2021-05-25 Lockheed Martin Corporation Hybrid elastomeric self-lubricated bearing
US11162553B2 (en) * 2019-02-12 2021-11-02 Deere & Company Externally-damped electromechanical valve assemblies
US10738852B1 (en) * 2019-03-29 2020-08-11 Aktiebolaget Skf Laminated bearing assembly with differing shim thicknesses
CN110701186B (zh) * 2019-09-29 2021-02-09 中国航发北京航空材料研究院 一种组合弹性轴承
CN110630631B (zh) * 2019-10-15 2022-08-26 上海电气集团股份有限公司 球关节及包括其的位置调整装置
US11732747B2 (en) * 2022-01-05 2023-08-22 Textron Innovations Inc. Journal bearings

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4268094A (en) * 1977-01-06 1981-05-19 Jerome Greene Radial and thrust-type hydrodynamic bearing capable of accommodating misalignment
US4424962A (en) * 1980-10-24 1984-01-10 Malcolm Johnston Spherical spring mounting
US5110259A (en) * 1989-10-13 1992-05-05 Bell Helicopter Textron Inc. Pitch change bearing system
US5460487A (en) * 1994-11-09 1995-10-24 United Technologies Corporation Pitch adjustment assembly for bearingless main rotors
US6695583B2 (en) * 2002-05-30 2004-02-24 Sikorsky Aircraft Corporation Snubber-vibration damper system for a bearingless main rotor

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3932059A (en) * 1975-01-10 1976-01-13 United Technologies Corporation Droop stops for helicopter rotor having elastomeric bearings
US4986735A (en) * 1989-10-13 1991-01-22 Bell Helicopter Textron, Inc. Pitch change bearing system
US5092738A (en) * 1990-04-06 1992-03-03 United Technologies Corporation Flexbeam helicopter rotor with improved snubber-vibration damper between the torque tube and the flexible spar member
US5265965A (en) * 1992-09-02 1993-11-30 Rexnord Corporation Composite ball and socket bearing with convex outer surface
US5913659A (en) * 1993-11-22 1999-06-22 United Technologies Corporation Apparatus and method for adjusting rotor blade tracking
US5902050A (en) * 1996-05-31 1999-05-11 Lord Corporation Spherical elastomeric bearing assembly
DE10324924B4 (de) * 2003-06-03 2021-08-26 Ab Skf Verfahren zum Ermitteln einer von einem Gleitlager mit sphärisch oder zylindrisch ausgebildeten Lagerflächen aufgenommenen Last
EP1704345B1 (en) * 2004-01-15 2012-03-07 Lord Corporation Rotary wing aircraft rod end and method of making a helicopter vehicle rod end with a precocked orientation
BRPI0706509A2 (pt) * 2006-01-11 2011-03-29 Fatigue Technology Inc kits de embuchamento, mancais e métodos de instalação
US8275585B2 (en) 2008-04-26 2012-09-25 Sikorsky Aircraft Corporation Spherical elastomeric bearing with improved shim thickness
KR101836992B1 (ko) * 2009-11-23 2018-03-09 로오드 코포레이션 로터리 윙 에어크래프트용 일래스토메릭 고 용량 적층식 로터리 윙 에어크래프트 베어링
EP2531725B1 (en) 2010-02-05 2014-04-16 Aktiebolaget SKF Hybrid wind turbine blade bearing
US9010679B2 (en) 2012-06-26 2015-04-21 Bell Helicopter Textron Inc. Hybrid spherical and thrust bearing
US10851838B2 (en) * 2014-01-28 2020-12-01 Triton Systems, Inc. Liner-as-seal bearings
US10309452B2 (en) * 2014-09-30 2019-06-04 Aktiebolaget Skf Cylindrical bearing with thermally conductive members

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4268094A (en) * 1977-01-06 1981-05-19 Jerome Greene Radial and thrust-type hydrodynamic bearing capable of accommodating misalignment
US4424962A (en) * 1980-10-24 1984-01-10 Malcolm Johnston Spherical spring mounting
US5110259A (en) * 1989-10-13 1992-05-05 Bell Helicopter Textron Inc. Pitch change bearing system
US5460487A (en) * 1994-11-09 1995-10-24 United Technologies Corporation Pitch adjustment assembly for bearingless main rotors
US6695583B2 (en) * 2002-05-30 2004-02-24 Sikorsky Aircraft Corporation Snubber-vibration damper system for a bearingless main rotor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170165520A1 (en) * 2015-12-09 2017-06-15 Ultimate Shoulder Exerciser, Inc. Exercise Device for the Shoulder
US20190144106A1 (en) * 2017-11-16 2019-05-16 Aktiebolaget Skf Combination elastomeric and ellipsoidal plain bearing
US10604244B2 (en) * 2017-11-16 2020-03-31 Aktiebolaget Skf Combination elastomeric and ellipsoidal plain bearing
US10371200B2 (en) * 2017-12-06 2019-08-06 Aktiebolaget Skf Combination elastomeric and cylindrical plain bearing
US11105381B2 (en) * 2020-02-04 2021-08-31 Aktiebolaget Skf Rotor assembly bearing with centrifugal clutch mechanism

Also Published As

Publication number Publication date
CN106151263B (zh) 2019-12-03
EP3056749B1 (en) 2020-04-08
CN106151263A (zh) 2016-11-23
US20160238069A1 (en) 2016-08-18
EP3056749A1 (en) 2016-08-17
US9709089B2 (en) 2017-07-18

Similar Documents

Publication Publication Date Title
US20160238068A1 (en) Combination spherical and laminated bearing
EP3115632B1 (en) Assembly with bearings or tolerance rings with functional layers
RU2526735C2 (ru) Узел для подкрепляющего кольца и способ его изготолвения
US10371200B2 (en) Combination elastomeric and cylindrical plain bearing
ES2903183T3 (es) Anillo de tolerancia
EP3486511B1 (en) Combination elastomeric and ellipsoidal plain bearing
RU2470200C2 (ru) Эластичный подшипник и способ его текущего ремонта и технического обслуживания
EP2799730B1 (en) Hybrid sliding element and elastomeric bearing
EP3152454A1 (en) Linear drive force overload protection device
WO2006018684A1 (en) A bush
JP6817539B2 (ja) トーショナルダンパ
KR102145490B1 (ko) 스프링 유닛, 스프링 어큐뮬레이터, 및 액추에이터
CA2961533C (en) A torsional vibration damper
US10344798B2 (en) Compact thrust bearing assemblies, mechanical assemblies including compact thrust bearing assemblies, and methods of providing limited rotational motion in a compact thrust bearing assembly
US10132348B2 (en) Bearing and bearing device
CN107076240B (zh) 具有减少撕裂的轮廓边缘的弹性体
CN113195929A (zh) 带有扭转止挡的弹性铰接部及其在减振器中的应用
US20110293210A1 (en) Centrifugal variable preload device
KR102482125B1 (ko) 스프링 히스테리시스 저감 장치
JP2007127148A (ja) ピストン軸受
JP2004108463A (ja) 樹脂製転がり軸受
GB2550135A (en) Axially Loaded spherical Joint assembly

Legal Events

Date Code Title Description
AS Assignment

Owner name: AKTIEBOLAGET SKF, SWEDEN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BOHM, ANTHONY CARL;REEL/FRAME:035146/0339

Effective date: 20150311

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION