WO2013008586A1 - 転がり軸受装置 - Google Patents
転がり軸受装置 Download PDFInfo
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- WO2013008586A1 WO2013008586A1 PCT/JP2012/065512 JP2012065512W WO2013008586A1 WO 2013008586 A1 WO2013008586 A1 WO 2013008586A1 JP 2012065512 W JP2012065512 W JP 2012065512W WO 2013008586 A1 WO2013008586 A1 WO 2013008586A1
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- Prior art keywords
- cage
- bearing device
- diameter side
- rolling bearing
- Prior art date
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
- F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
- F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/3887—Details of individual pockets, e.g. shape or ball retaining means
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6607—Retaining the grease in or near the bearing
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6607—Retaining the grease in or near the bearing
- F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6622—Details of supply and/or removal of the grease, e.g. purging grease
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
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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
- F16C2204/00—Metallic materials; Alloys
- F16C2204/60—Ferrous alloys, e.g. steel alloys
- F16C2204/66—High carbon steel, i.e. carbon content above 0.8 wt%, e.g. through-hardenable steel
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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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/30—Fluoropolymers
- F16C2208/32—Polytetrafluorethylene [PTFE]
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/47—Cosmonautic vehicles, i.e. bearings adapted for use in outer-space
Definitions
- the present invention relates to a rolling bearing device, and more particularly to a rolling element guide type cage structure in a rolling bearing device in which grease is supplied from an inner ring spacer to a cage.
- a large amount of fluid lubricant is used in bearings that are used in low-temperature and high-speed rotation environments such as rocket engine liquid fuel turbo pumps and in bearings that are used in vacuum environments such as space equipment. It is conceivable that the spacer is provided on the inner ring side with an oil puddle inside which contains lubricating oil, and the lubricating oil is supplied by utilizing the centrifugal force associated with the rotation of the bearing. Proposed such a configuration in a previous application (Japanese Patent Application No. 2010-227652).
- Patent Document 1 in an angular contact ball bearing having a cage guided on the inner peripheral surface of an outer ring, grease is contained inside the bearing for the purpose of suppressing an annoying noise, that is, a cage noise in a low speed operation region.
- a lubricant supply mechanism for supplying a base oil of grease to the guide surface portion of the inner peripheral surface of the outer ring is provided.
- a grease pool in the form of a circumferential groove is provided on the inner peripheral surface of the cage, and the base oil of the grease is supplied to the inner peripheral surface of the outer ring through a through hole provided in the cage. (See FIGS. 9 to 13 of Patent Document 1).
- Patent Document 2 discloses a ball bearing using a space between adjacent pockets of a cage as a grease pool.
- the inner circumferential surface and outer circumferential surface of the cage are provided with circumferential streaks, and the base oil separated from the grease retained in the grease pool is allowed to flow into the streaks, and the rolling elements along the streaks. It is designed to be supplied to the surface.
- a cage used for a grease lubricated bearing is a rolling element guide, and a claw for preventing the rolling element from falling is provided over the entire circumference of a pocket that accommodates the rolling element (see FIG. 14). For this reason, even if grease or grease base oil is supplied from the inner ring spacer to the cage, it adheres to the rolling elements, but is scraped off by the retaining claws and supplied to the raceway surface, especially the outer ring raceway surface. There is a problem that is disturbed.
- the rolling bearing disclosed in Patent Document 1 has a unique problem of cage noise because the cage guide is the outer ring guide.
- grease is supplied to the outer ring guide surface, but it is not supplied to the raceway surface. Further, in order to promote the supply of grease and base oil, it is necessary to increase the size and number of through holes provided in the cage, which causes a manufacturing problem.
- the rolling bearing disclosed in Patent Document 2 also uses a crown-shaped cage that holds a rolling element in a pocket having a partially spherical inner peripheral surface, and is therefore caused by the rolling element guide. It does not solve the above-mentioned problem, that is, the problem that the grease adhering to the rolling elements is scraped off by the retaining claws and the supply to the raceway surface is hindered.
- the technical means of using the capillary phenomenon to supply the base oil separated from the grease to the rolling elements through the lines extending in the circumferential direction reduces the amount of base oil supplied to the raceway surface and provides good lubrication. Not enough to maintain.
- a main object of the present invention is to provide a structure that facilitates supplying grease supplied from an inner ring spacer to an outer ring raceway surface in a rolling bearing device having a rolling element guide type cage.
- the retaining portion of the rolling element guide retainer is provided only on the pair of pocket inner wall faces facing the circumferential direction of the retainer, and falls on the pair of pocket inner wall faces facing the cage axial direction.
- the problem is solved by forming a relatively large radial passage that penetrates from the inner diameter side of the cage to the outer diameter side without providing a stop portion.
- the rolling bearing device of the present invention includes an inner ring 2 having a raceway surface 2a on the outer periphery, an inner ring spacer 3 that contacts the end surface of the inner ring 2 and rotates together with the inner ring 2, and an outer ring 4 that has a raceway surface 4a on the inner periphery.
- grease is supplied from the inner ring spacer 3 to the cage 8 using centrifugal force, and the inner diameter side of the cage 8 is interposed between the inner wall surface of the pocket 10 and the rolling element 6.
- the radial passage 22 penetrating from the outer diameter side to the outer diameter side, the radial passage 22 is used as a grease pool and also used as a grease passage for moving the grease adhering to the rolling elements 6 to the outer ring raceway surface 4a.
- the radial passage 22 faces the segment-shaped clearance 20 between the arc-shaped portion 16 formed at the four corners of the pocket 10 and the rolling element 6 and the cage axial direction of the pocket 10. It comprises an arcuate clearance 18 between the first inner wall surface portion 14 and the rolling element 6.
- the grease supplied from the inner ring spacer can be easily supplied to the outer ring raceway surface. That is, the grease supplied to the outer diameter side from the inner ring spacer 3 by the action of the centrifugal force moves to the inner peripheral surface of the cage 8 and at the same time the radial passage between the pocket 10 of the cage 8 and the rolling element 6. 22 (the arc-shaped clearance 18 and the segment-shaped clearance 20) are collected and supplied to the raceway surface 4a of the outer ring 4 from there. Therefore, the grease supplied from the inner ring spacer to the cage is not hindered from moving from the inner diameter side to the outer diameter side of the cage and thus to the outer ring raceway surface by the locking part as in the conventional case. .
- FIG. 1B and FIG. 14 show a comparison between a rolling bearing according to the present invention and a rolling bearing according to the prior art.
- the cage containing the rolling elements is viewed from the inner diameter side, but in FIG. 14 showing the prior art, there is only a slight guide clearance between the retaining claw of the cage and the rolling elements. There is no space penetrating in the radial direction of the cage.
- the conventional technology although there is a guide clearance between the locking part and the rolling element, it is up to a minute gap, and is curved along the surface of the rolling element and linearly in the radial direction. There is no penetration.
- the space has a remarkably large cross-sectional area as compared with the guide clearance in the prior art, and therefore plays a role of promoting and promoting the movement of the grease from the inner diameter side to the outer diameter side of the cage 8.
- FIG. 1A It is sectional drawing which shows the Example of this invention. It is the figure which looked at the holder
- FIG. 6A It is a fragmentary sectional view similar to FIG. 6A. It is a fragmentary sectional view similar to FIG. 6B. It is a fragmentary sectional view of a holder. It is a fragmentary sectional view of a holder. It is sectional drawing of a rolling bearing. It is a fragmentary perspective view of a holder
- the rolling bearing device shown in FIGS. 2A and 2B is applied to a bearing for a liquid fuel turbo pump of a rocket engine used in a low temperature and high speed environment, and includes a double row angular ball bearing 1.
- the angular ball bearing has a contact angle.
- the contact angle is an angle formed by a plane (radial plane) perpendicular to the center axis of the bearing and an action line (indicated by a one-dot chain line in FIG. 2A) of the resultant force transmitted to the rolling elements by the race rings (inner ring, outer ring). Is defined.
- Each angular ball bearing 1 has an inner ring 2, an outer ring 4, rolling elements 6 and a cage 8 as main components.
- the inner ring 2 has a raceway surface 2 a on the outer periphery, and is fixed to a rotating shaft (not shown) with an inner ring spacer 3 interposed between the pair of inner rings 2.
- the outer ring 4 has a raceway surface 4 a on the inner periphery, and is fixed to a housing (not shown) with an outer ring spacer 5 interposed between the pair of outer rings 4.
- the plurality of rolling elements 6 are interposed between the raceway surface 2a of the inner ring 2 and the raceway surface 4a of the outer ring 4, and contact each raceway surface 2a, 4a with a contact angle (angular contact).
- the cage 8 is between the inner ring 2 and the outer ring 4 and has a pocket 10 for accommodating the rolling elements 6 as shown in FIG. 3, and holds the plurality of rolling elements 6 at predetermined intervals in the circumferential direction. Play a role.
- Reference numeral 9 denotes a column between the pocket 10 and the pocket 10 of the cage 8.
- the inner ring spacer 3 has a cylindrical shape, and both end surfaces are in contact with the end surfaces of the double row inner rings 2 to position the inner ring 2 in the axial direction.
- the inner ring 2 is in the form of a so-called shoulder inner ring in which the shoulder on the bearing inner side that does not make angular contact with the rolling element 6 is cut off. Therefore, the rolling element 6 is positioned on the radially outer side of the inner ring spacer 3, and the surface of the rolling element 6 faces the outer periphery of the end of the inner ring spacer 3.
- the outer ring spacer 5 has a cylindrical outer peripheral surface, and a protruding portion 5a protruding toward the inner diameter side is provided at the center of the cylindrical inner peripheral surface.
- the outer ring 4 is inserted into the cylindrical inner peripheral surface of the outer ring spacer 5, and an elastic member such as a disc spring 7 is disposed between the outer ring 4 and the protruding portion 5a to apply a bearing preload.
- both sides of the bearing device in the axial direction are generally sealed by a sealing device. This is to prevent the lubricant from scattering to the outside of the bearing and to prevent foreign matter from entering from the outside.
- a well-known sealing device can be selected and employed.
- the outer diameter end of the seal or shield is attached to the groove 4b formed on the inner peripheral surface of the shoulder of the outer ring 4, and the inner end faces the groove 2b formed on the outer peripheral surface of the shoulder of the inner ring 2, so A sealing device is configured.
- the sealing device can be omitted.
- the cage 8 can be made of resin, and can be formed of, for example, a composite material in which glass fiber or carbon fiber is added to PEEK or the like. Alternatively, the cage 8 can be formed of a metal material such as carburized steel, aluminum alloy, stainless steel, or copper alloy. In order to reduce friction at the initial stage of rotation, it is preferable to form a solid lubricant film made of PTFE or the like on at least one of the inner ring raceway surface 2a, the outer ring raceway surface 4a, and the surfaces of the rolling elements 6.
- a solid lubricating film made of PTFE or the like may be formed on the entire surface including the pocket inner surface of the cage 8. It is also effective to apply grease in advance to the inner ring raceway surface 2a and the outer ring raceway surface 4a.
- the inner ring spacer 3 has a double cylindrical shape composed of an inner cylinder 3a and an outer cylinder 3b.
- a grease pool portion 3c is formed between the inner cylinder 3a and the outer cylinder 3b.
- the grease pool portion 3c is formed by forming an annular groove on the outer periphery of the inner cylinder 3a and covering with the outer cylinder 3b, and functions as a space for enclosing grease.
- a plurality of grooves 3d extending from the grease reservoir 3c to the end surface of the inner cylinder 3a are provided in the circumferential direction on the outer peripheral surface of the inner cylinder 3a. The grooves 3d communicate with the grease reservoir 3c.
- the inner cylinder 3a and the outer cylinder 3b are opened at a step X portion, and the opening functions as a grease discharge groove (hereinafter, the reference numeral 3d is also used as the grease discharge groove). That is, the amount of grease discharged during rotation can be adjusted by adjusting the total opening amount of the grease discharge groove 3d.
- the outer cylinder 3b has a cylindrical shape and is made of a resin or a metal material.
- the end portion of the outer cylinder 3 b is relatively chamfered to prevent interference with the rolling element 6, while bringing the end surface of the outer cylinder 3 b closer to the end surface of the inner ring 2.
- the length L 2 of the outer cylinder 3b is shorter than the length L 1 of the inner cylinder 3a (L 1 > L 2 ), and the level difference between the end surface of the inner cylinder 3a and the end surface of the outer cylinder 3b is determined. This is indicated by the symbol X in FIG.
- both end surfaces of the inner cylinder 3a come into contact with the end surfaces of the inner ring 2 to position the inner ring 2 in the axial direction.
- a clearance S is formed over the entire circumference between the end surface of the inner ring 2 and the end surface of the outer cylinder 3b.
- the symbol X also means the width dimension of the clearance S.
- the clearance S is referred to as a grease supply path.
- the inner ring 2 is a so-called shoulder inner ring
- the surface of the rolling element 6 is brought close to the outer periphery of the end of the inner ring spacer 3, so that the grease supply path S is formed from the grease discharge groove 3d.
- the grease that has flowed out to the outer diameter side easily adheres to the surface of the rolling element 6, and further flows to reach the inner ring raceway surface 2a and the outer ring raceway surface 4a, where lubrication is performed.
- the angular ball bearing 1 on the left side of the figure shows a state in which the rolling elements 6 are removed.
- 1B and 3 are views of the cage 8 in FIG. 1A as viewed from the inner diameter side.
- the outline of the pocket 10 of the cage 8 is substantially rectangular, and a pair of inner wall surface portions 12 facing the circumferential direction of the cage 8 and a pair of inner wall portions facing the axial direction of the cage 8. It consists of the wall surface part 14 and the arc-shaped part 16 located in the four corners of a rectangle.
- the inner wall surface portion 12 facing the circumferential direction of the cage is also the side surface of the column 9 between the adjacent pockets 10.
- each of the pair of inner wall surfaces 12 facing each other in the circumferential direction of the cage has a central arc portion 12a and linear portions 12b on both sides thereof.
- the radius of curvature of the circular arc portion 12a is larger than the radius of curvature of the rolling element 6, and is in a dimensional relationship such that a predetermined guide clearance is formed between the rolling element (ball) 6 in a natural state. If a specific example is given about the angular ball bearing of the nominal number 7009, the diameter of the rolling element 6 is 9.525 mm, and the distance between the opposing surfaces of the linear part 12b is 7.09 mm.
- Each of the pair of inner wall surfaces 14 facing each other in the cage axial direction has a central arc portion 14a and linear portions 14b on both sides thereof.
- the radius of curvature of the arc portion 14 a is equal to the radius of curvature of the arc portion 12 a and is larger than the radius of curvature of the rolling element 6. Therefore, as is apparent from FIG. 1B, an arc-shaped clearance 18 is formed between the rolling elements 6. If a specific example is given about the angular ball bearing of the nominal number 7009, the distance between the opposing surfaces of the linear portion 14b is 9.20 mm.
- the arc-shaped portions 16 located at the four corners of the pocket 10 are in the form of so-called Nusumi.
- a segment-shaped gap 20 is formed between the arc-shaped portion 16 and the rolling element 6.
- the arc-shaped clearance 18 and the segment-shaped clearances 20 at both ends thereof constitute a set of radial passages 22.
- a radial passage 22 having a relatively large cross-sectional area penetrating from the side to the outer diameter side is secured, and the radial passage 22 is used to promote and promote the movement of the grease in the radial direction of the cage.
- FIG. 1B and FIG. 14 are views of the state in which the rolling elements are accommodated in the pockets of the cage as viewed from the inner diameter side of the cage, and show a comparison between the example and the comparative example.
- FIG. 14 showing the comparative example there is no clearance between the pocket and the rolling element
- FIG. 1B showing the example a relatively large clearance is formed on the left and right of the rolling element 6 in FIG. It can be seen that 22 is formed.
- the radial passage 22 is used as a grease pool, and also as a grease passage for allowing the grease adhering to the rolling elements 6 to move further toward the outer ring raceway surface 4a.
- the grease that flows out from the grease discharge groove 3d of the inner ring spacer 3 due to the centrifugal force and is supplied to the outer diameter side through the grease supply path S moves to the inner peripheral surface of the cage 8 and retains the cage.
- 8 is accumulated in the radial passage 22 (arc-shaped clearance 18, segment-shaped clearance 20) between the pocket 10 and the rolling element 6, and is further supplied to the raceway surface 4a of the outer ring 4 and falls as in the conventional case.
- the stopper does not hinder the movement of the cage from the inner diameter side to the outer diameter side.
- two rows of inner diameter side annular grooves 24 are formed on the inner periphery of the cage 8.
- the inner diameter side annular grooves 24 are arranged in parallel with each other so as to avoid the central portion in the width direction of the cage 8.
- the inner wall surface portion 14 facing the cage axial direction is within the width of the inner diameter side annular groove 24.
- the radial passage 22 is opened in the inner annular groove 24.
- the central portion sandwiched between the two rows of the inner diameter side annular grooves 24 swells like a ridge if the inner diameter side annular grooves 24 serve as gaps, that is, has a smaller diameter than the inner diameter side annular grooves 24.
- the inner diameter of the central portion is indicated by reference sign d 1
- the inner diameter of the inner diameter side annular groove 24 is indicated by reference sign d 2 .
- the end face facing the pocket 10 in the central portion corresponds to a locking portion 12d described below. Therefore, what is indicated by reference sign d 1 is the inner diameter of the stopper 12d.
- the arc portion 12a of the inner wall surface portion 12 facing the cage circumferential direction can be further divided into a guide portion 12c located on the cage outer diameter side and a retaining portion 12d located on the cage inner diameter side.
- the guide part 12c is a part cylindrical surface having a larger diameter than the rolling element 6, and is a part that contacts and guides the rolling element 6 when the bearing rotates.
- the falling stop portion 12d has a smaller diameter than the rolling element 6 as it goes to the inner diameter side of the cage. For this reason, the stopper 12d plays a role of preventing the rolling element 6 from falling to the inner diameter side of the cage. Specifically, it has a conical shape as shown in FIGS. 4A and 4B or a spherical shape as shown in FIGS. 5A and 5B.
- the retaining portion 12d is within the width of the inner diameter side annular groove 24 and is convex toward the inner diameter side of the cage, so that the volume of the inner diameter side annular groove 24 is reduced. .
- the inner diameter d 1 of the retaining portion it is necessary to increase the inner diameter d 1 of the retaining portion, and considering the manufacturing surface, it is desirable to match the inner diameter d 2 of the inner diameter side annular groove 24.
- the inner peripheral surface shape of the locking part 12d is a conical surface shape (FIG. 4A), as is apparent from a comparison between FIG. 4B and FIG. 5B.
- the arc portion 14a of the inner wall surface portion 14 has no stopper.
- FIGS. 7A and 7B an example in which such a locking portion is provided.
- the inner wall surface portion 14 is not provided with a locking portion regardless of whether it is conical or spherical, thereby increasing the volume of the radial passage 22 and increasing the amount of grease retained.
- the entrance of the arc-shaped clearance 18 of 22 is widened, it is possible to smoothly accept the ingress of grease supplied from the inner ring spacer 3.
- FIG. 8 shows an example in which a cut-out groove 26 is provided in the annular groove 24 on the inner diameter side so that the arc-shaped portions 16 adjacent to each other in the circumferential direction, and therefore the segment-shaped gaps 20 communicate with each other.
- the cut-out groove 26 serves to guide the grease in the inner diameter side annular groove 24 to the segment clearance 20.
- FIG. 9 shows an example in which the arc portion 14 a of the inner wall surface portion 14 is connected to the inner diameter side annular groove 24 via the inclined surface 28.
- the slope 28 acts to smoothly guide the grease in the inner diameter side annular groove 24 to the arc-shaped gap 18.
- 10A and 10B show an example in which an outer diameter side annular groove 30 is formed on the outer peripheral surface of the cage 8.
- the width of the outer diameter side annular groove 30 extends beyond the radial passage 22 (the arc-shaped clearance 18 and the segment-shaped clearance 20) to the end face side of the cage 8.
- the outer diameter side annular groove 30 By providing the outer diameter side annular groove 30, the grease to be supplied to the outer diameter raceway surface 4 a through the radial passage 22 is blocked by both side walls of the outer diameter side annular groove 30. 8 can be prevented from flowing out in the width direction.
- the outer ring 4 preferably has shoulders 4c on both shoulders, that is, on both sides of the raceway surface 4a.
- the shoulder surface 4c is made to correspond to the side wall of the outer diameter side annular groove 30, and the outer diameter side annular groove 30 is covered. This is advantageous for reliably preventing the formed grease from flowing out in the width direction of the cage.
- 11A and 11B show an inclined surface in which the outer circumferential side annular groove 30 has a downward slope toward the pocket 10 on the advancing side in the cage rotation direction of each pocket 10 and a width gradually narrowing toward the pocket 10.
- the example which provided 32 is shown.
- What is indicated by reference numeral 34 is a step formed to reduce the width of the inclined surface 32.
- 11A and 11B are examples in the case of a unidirectional rotary bearing as indicated by the symbol o in FIG. 11A, so there is only one inclined surface 32 in each pocket 10, but in the case of a bidirectional rotary bearing,
- the inclined surfaces 32 are provided on both sides in the circumferential direction.
- FIG. 12A shows an example in which a corner cut portion 36 is provided at the intersection of the raceway surface 4a of the outer ring 4 and the shoulder surface 4c.
- the corner cut portion 36 is larger than a normal chamfer.
- the corner cut portion may be symmetrical on the left and right of the figure as shown in FIG. 12A, or may be asymmetric as shown in FIG. 12B.
- the corner cut portion 38 on the side farther from the intersection is larger than the side closer to the intersection between the line of action of the force transmitted to the rolling element 6 (indicated by the alternate long and short dash line) and the raceway surface 4a. Also good.
- the corner cut portion 38 By enlarging the corner cut portion 38, the grease moved from the outer diameter side annular groove 30 of the cage 8 to the outer ring 4 side can be easily drawn into the raceway surface 4a and further to the back of the raceway surface 4a.
- FIG. 13 shows an example in which a plurality of inclined grooves 40 are provided on the shoulder surface 4 c of the outer ring 4.
- the inclined groove 40 is not a cut-through groove, one end is open to the raceway surface 4 a, but the other end ends before the end surface of the outer ring 4.
- the inclined groove 40 is inclined with respect to the axis of the outer ring 4, and when viewed in the cage rotation direction, the outer ring end surface side is on the delay side and the raceway surface side is on the advance side.
- the inclined groove 40 can be curved as well as linear as shown.
- the grease moved from the outer diameter side annular groove 30 to the outer ring 4 side moves along the inclined groove 40 and is guided to the raceway surface 4a. Since the inclined groove 40 is not cut through to the end surface of the outer ring 4, it is possible to prevent the grease that has moved from the outer diameter side annular groove 30 to the outer ring 4 side from flowing out in the width direction.
- the inclination direction of the inclined groove 40 is such that the raceway surface side is on the leading side and the outer ring end surface side is on the lagging side when viewed in the cage rotation direction, so that grease moves from the outer ring end surface side to the raceway surface side as the cage rotates. The force to act acts.
- the embodiment applied to the double row angular contact ball bearing applied to the liquid fuel turbo pump bearing of the rocket engine used in the environment of low temperature and high speed rotation is taken as an example. Is not limited thereto, and can be widely applied to rolling bearings used for various purposes.
- angular ball bearings double row or single row
- the present invention can be applied to other bearing types (for example, deep groove ball bearings), and equivalent effects can be expected. Needless to say.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
すなわち、この発明の転がり軸受装置は、外周に軌道面2aをもつ内輪2と、内輪2の端面に接して内輪2と共に回転する内輪間座3と、内周に軌道面4aをもつ外輪4と、内輪2の軌道面2aと外輪4の軌道面4aとの間に介在する複数の転動体6と、内輪2と外輪4との間にあって転動体6を収容する複数のポケット10をもつ保持器8とを有するものにおいて、遠心力を利用して内輪間座3から保持器8へ向けてグリースを供給するとともに、ポケット10の内壁面と転動体6との間に、保持器8の内径側から外径側まで貫通した半径方向通路22を設けることにより、前記半径方向通路22をグリースたまりとして活用するともに、転動体6に付着したグリースを外輪軌道面4aに移動させるためのグリース通路として活用するようにしたものである。前記半径方向通路22は、より詳しくは、前記ポケット10の四隅に形成した円弧状部分16と前記転動体6との間のセグメント状すきま20、および、前記ポケット10の保持器軸方向に向かい合った第一の内壁面部分14と前記転動体6との間の弧状すきま18とからなる。
2 内輪
2a 内輪軌道面
2b 溝
3 内輪間座
3a 内筒
3b 外筒
3c グリースたまり部
3d グリース吐出溝
S グリース供給路
4 外輪
4a 外輪軌道面
4b 溝
4c 肩面
5 外輪間座
6 転動体(玉)
7 弾性部材(皿ばね)
8 保持器
9 柱
10 ポケット
12 保持器円周方向に向かい合った内壁面部分
12a 円弧部分
12c 案内部
12d 落ち止め部
12b 直線部分
14 保持器軸方向に向かい合った内壁面部分
14a 円弧部分
14b 直線部分
16 円弧状部分
18 弧状すきま
20 セグメント状すきま
22 半径方向通路
24 内径側環状溝
26 切り通し溝
28 斜面
30 外径側環状溝
32 傾斜面
34 段差
36 コーナーカット部(対称)
38 コーナーカット部(非対称)
40 傾斜溝
Claims (17)
- 外周に軌道面をもつ内輪と、内輪の端面に接して内輪と共に回転する内輪間座と、内周に軌道面をもつ外輪と、内輪の軌道面と外輪の軌道面との間に介在する複数の転動体と、内輪と外輪との間にあって転動体を収容する複数のポケットをもつ保持器とを有し、遠心力を利用して前記内輪間座から前記保持器へ向けてグリースを供給するとともに、前記ポケットの内壁面と前記転動体との間に、前記保持器の内径側から外径側まで貫通した半径方向通路を設けることにより、前記半径方向通路をグリースたまりとして活用するとともに、前記転動体に付着したグリースを前記外輪の軌道面に移動させるためのグリース通路として活用するようにした転がり軸受装置。
- 前記半径方向通路は、前記ポケットの四隅に形成した円弧状部分と前記転動体との間のセグメント状すきま、および、前記ポケットの内壁面のうち保持器軸方向に向かい合った第一の内壁面部分と前記転動体との間の弧状すきまとからなる請求項1の転がり軸受装置。
- 前記保持器の内周に内径側環状溝を形成し、前記半径方向通路を前記内径側環状溝に少なくとも部分的に開口させた請求項1または2の転がり軸受装置。
- 前記ポケットの内壁面のうち保持器円周方向に向かい合った第二の内壁面部分は、中央の円弧部分とその両側の直線部分とからなり、前記円弧部分は、保持器外径側に位置して前記転動体よりも大径の部分円筒面状の案内部と、保持器内径側に位置して保持器内径側にいくほど前記転動体よりも小径となった落ち止め部とからなる請求項1、2または3の転がり軸受装置。
- 前記落ち止め部は部分球面状である請求項4の転がり軸受装置。
- 前記ポケットの第一の内壁面部分は、中央に位置する円弧部分とその両側の直線部分とからなり、前記円弧部分は部分円筒面状の部分のみからなる請求項1、2または3の転がり軸受装置。
- 前記内径側環状溝に、前記ポケットの四隅の円弧状部分のうち保持器円周方向で隣り合った円弧状部分同士を連通させる切り通し溝を設けた請求項3ないし6のいずれか1項の転がり軸受装置。
- 前記ポケットの第一の内壁面部分の前記部分円筒面状の部分は斜面を介して前記内径側環状溝と接続している請求項4ないし6のいずれか1項の転がり軸受装置。
- 前記保持器の外周面に前記半径方向通路を超える幅寸法の外径側環状溝を形成した請求項1ないし8のいずれか1項の転がり軸受装置。
- 前記外輪は前記軌道面の両側に肩をもつ請求項1ないし9のいずれか1項の転がり軸受装置。
- 前記外径側環状溝の各ポケットの保持器回転方向の進み側に、前記ポケットに向かって下り勾配で、前記ポケットに向かって幅が徐々に狭くなった傾斜面を設けた請求項9または10の転がり軸受装置。
- 前記外輪の軌道面と肩面との交点にコーナーカット部を設けた請求項10または11の転がり軸受装置。
- 前記コーナーカット部を非対称とし、転動体へ伝えられる力の合力の作用線と軌道面との交点に近い側よりも前記交点から遠い側のコーナーカット部を大きくした請求項12の転がり軸受装置。
- 前記外輪の肩面に、外輪軸線に対して傾斜し、保持器回転方向で見て外輪端面側よりも軌道面側が進み側にある、軌道面側に開口した傾斜溝を設けた請求項10ないし13のいずれか1項の転がり軸受装置。
- 前記傾斜溝は前記外輪の端面の手前で終わっている請求項14の転がり軸受装置。
- 前記内輪、前記外輪、前記転動体の材質はマルテンサイト系ステンレス鋼で、前記内輪の軌道面および前記外輪の軌道面ならびに前記転動体の表面にPTFE被膜を施した請求項1ないし15のいずれか1項の転がり軸受装置。
- あらかじめグリースを塗布した請求項1ないし16のいずれか1項の転がり軸受装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP12810623.4A EP2733373B1 (en) | 2011-07-13 | 2012-06-18 | Rolling bearing unit |
US14/129,626 US9206848B2 (en) | 2011-07-13 | 2012-06-18 | Rolling bearing unit |
RU2014105282/11A RU2585125C2 (ru) | 2011-07-13 | 2012-06-18 | Узел подшипника качения |
CN201280034032.2A CN103748372B (zh) | 2011-07-13 | 2012-06-18 | 滚动轴承装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011-154901 | 2011-07-13 | ||
JP2011154901A JP5774395B2 (ja) | 2011-07-13 | 2011-07-13 | 転がり軸受装置 |
Publications (1)
Publication Number | Publication Date |
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WO2013008586A1 true WO2013008586A1 (ja) | 2013-01-17 |
Family
ID=47505884
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2012/065512 WO2013008586A1 (ja) | 2011-07-13 | 2012-06-18 | 転がり軸受装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US9206848B2 (ja) |
EP (1) | EP2733373B1 (ja) |
JP (1) | JP5774395B2 (ja) |
CN (1) | CN103748372B (ja) |
RU (1) | RU2585125C2 (ja) |
WO (1) | WO2013008586A1 (ja) |
Families Citing this family (9)
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DE102015201101A1 (de) * | 2015-01-23 | 2016-07-28 | Schaeffler Technologies AG & Co. KG | Wälzlager |
DE102015223255A1 (de) * | 2015-11-25 | 2017-06-01 | Schaeffler Technologies AG & Co. KG | Kugellagerkäfig |
DE102015224859A1 (de) * | 2015-12-10 | 2017-06-14 | Schaeffler Technologies AG & Co. KG | Kugellagerkäfig |
US10415646B2 (en) * | 2016-09-16 | 2019-09-17 | Steering Solutions Ip Holding Corporation | Telescoping roller I-shaft and method of assembly |
JP6874455B2 (ja) * | 2017-03-22 | 2021-05-19 | 株式会社ジェイテクト | 転がり軸受 |
US10654569B2 (en) * | 2018-07-30 | 2020-05-19 | Textron Innovations Inc. | Mast bearing system for a tiltrotor aircraft |
PL240712B1 (pl) * | 2020-03-12 | 2022-05-23 | Mateusz Kusznierewicz | Łożysko toczne |
FR3112824B1 (fr) * | 2020-07-27 | 2023-01-20 | Safran Aircraft Engines | Cage de roulement avec dispositif de lubrification |
CN113933053B (zh) * | 2021-09-15 | 2024-03-19 | 东北林业大学 | 非接触感应式摩擦电轴承传感器及其测试方法 |
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Also Published As
Publication number | Publication date |
---|---|
JP5774395B2 (ja) | 2015-09-09 |
RU2585125C2 (ru) | 2016-05-27 |
EP2733373A4 (en) | 2015-08-05 |
US9206848B2 (en) | 2015-12-08 |
EP2733373A1 (en) | 2014-05-21 |
US20140219596A1 (en) | 2014-08-07 |
CN103748372A (zh) | 2014-04-23 |
EP2733373B1 (en) | 2018-02-21 |
JP2013019511A (ja) | 2013-01-31 |
RU2014105282A (ru) | 2015-08-20 |
CN103748372B (zh) | 2017-09-29 |
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