WO2017110905A1 - Palier à roulement - Google Patents

Palier à roulement Download PDF

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Publication number
WO2017110905A1
WO2017110905A1 PCT/JP2016/088171 JP2016088171W WO2017110905A1 WO 2017110905 A1 WO2017110905 A1 WO 2017110905A1 JP 2016088171 W JP2016088171 W JP 2016088171W WO 2017110905 A1 WO2017110905 A1 WO 2017110905A1
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WO
WIPO (PCT)
Prior art keywords
ring
cage
roller bearing
guided
annular
Prior art date
Application number
PCT/JP2016/088171
Other languages
English (en)
Japanese (ja)
Inventor
貴行 鈴木
清茂 山内
Original Assignee
Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2017110905A1 publication Critical patent/WO2017110905A1/fr

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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
    • F16C19/22—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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly 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
    • 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
    • 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
    • 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
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

Definitions

  • the present invention relates to a roller bearing suitable for a revolving part such as a planetary rotating body provided in a planetary speed reducer, and particularly to guiding a cage.
  • planetary speed reducers that provide a large reduction ratio are arranged inside the wheel rim.
  • the planetary rotating body provided in the planetary reduction gear is composed of a planetary gear or a planetary roller that revolves while rotating between a ring gear and a sun gear, and is supported by a carrier pin via a rolling bearing.
  • a rolling bearing a roller bearing such as a tapered roller bearing or a cylindrical roller bearing is employed (for example, Patent Documents 1 and 2 below).
  • roller bearings are provided with a cage for maintaining a circumferential interval between the rollers.
  • pockets for storing rolling elements are formed at equal intervals in the circumferential direction.
  • rolling bearings are included in the cage and the lubricating oil inside the bearing. Centrifugal force by revolving together with the planetary rotating body also acts. The centrifugal force due to the revolving motion causes a load region in the rolling bearing and causes deformation and eccentricity of the cage and bias of the lubricating oil inside the bearing.
  • the roller bearing disclosed in Patent Document 3 forms a guided surface composed of a plate-thick surface at the tip of a protruding piece that is partially cut and raised from a small-diameter side annular portion of a steel plate cage, and the outer ring of the inner ring or the outer ring
  • a cage guide surface is formed on the inner periphery, and the cage can be guided by contact between the guided surface and the cage guide surface.
  • a cage guide surface is formed on the outer periphery of the outer ring, and a guided surface that faces the cage guide surface in the radial direction is formed on an extended portion of the annular portion of the cage.
  • the cage can be guided by contact between the guided surface and the cage guide surface.
  • the roller bearing disclosed in Patent Document 4 guides the cage on the outer circumference of the outer ring, at least one of the annular portions of the cage is opposed to the cage guide surface on the outer circumference of the outer ring in the radial direction. There is a concern that the total width of the bearing may be increased. Further, since the cage extension part passes on the outer diameter side of the outer ring through the outer diameter side of the outer ring, the side surface of the outer ring on the inner diameter small diameter side cannot be fixed by abutting against other members such as the housing shoulder. . For this reason, the combination of the pair of roller bearings is limited to the front combination, and a preload cannot be applied to the roller bearings. If preload is not applied to the roller bearing, the support of the planetary rotating body may not be stable due to the internal clearance of the positive bearing, which may interfere with the normal operation of the planetary rotating body, for example, the normal meshing of the planetary gear. .
  • the cage is guided by contact between the guided surface formed of the plate thickness surface of the projecting piece obtained by cutting and raising the small-diameter side annular portion of the cage and the inner periphery of the outer ring.
  • the cage is inclined when the centrifugal force is large, and the contact area between the guided surface and the inner circumference of the outer ring is a line.
  • the contact area is narrowed, there is a concern that the contact surface pressure increases or the oil film is cut and wear or seizure occurs.
  • the roller irregularly interferes with the column part the column part may be abnormally worn.
  • the problem to be solved by the present invention is that even when the planetary rotating body provided in the planetary reduction gear is supported by the roller bearing, the cage guide portion is worn and seized, and the cage column is abnormal. It is to prevent wear.
  • a roller bearing including an inner ring, an outer ring, a plurality of rollers interposed between the inner ring and the outer ring, and a cage that holds the rollers.
  • the cage has an integrally formed cage body, and a first ring and a second ring fixed to the cage body, and the cage body has a first annular portion and a second annular portion. And a pillar portion that divides the two annular portions into pockets, the first ring is fixed to the first annular portion, and the second ring is fixed to the second annular portion.
  • a cage guide surface for guiding the cage in the radial direction is provided only on an inner periphery of the outer ring, and the guided surface guided by the cage guide surface is the cage.
  • Inner surface has a low coefficient of friction than the surface of said retainer body is obtained by adopting the configuration that.
  • the cage guide surface is provided on the outer ring and the guided surface is provided on the cage, so the cage is guided by the outer ring.
  • the cage between the outer ring and the guided surface of the cage is compared with the inner ring guide.
  • the relative speed difference between the cage surface and the cage guide surface and guided surface becomes longer and the contact surface pressure decreases (so-called PV value suppression), so that the guided surface and cage guide surface wear. And seizure is prevented.
  • the cage guide surface is provided on the inner circumference of the outer ring, the lubricating oil moves to the inner circumference side of the outer ring by the action of a large centrifugal force accompanying the revolution movement of the planetary rotating body.
  • the lubricity of the guided surface is improved. This is also effective in preventing wear and seizure of the guided surface and the cage guide surface in the support application of the planetary rotor.
  • the guided surface can be provided with an arbitrary material on the first ring and the second ring which are separate parts from the cage body, the guided surface has a lower coefficient of friction than the surface of the cage body. be able to.
  • the guided surface and the cage guiding surface can be contacted on both sides in the axial direction of the cage with the pocket as a boundary, a large centrifugal force due to the revolving motion of the planetary rotating body acted on the cage. Even in this case, the tilt of the cage can be suppressed. As a result, a decrease in the contact area between the guided surface and the cage guide surface is suppressed, and abnormal contact with the column portion is also prevented, so that the guided surface and the cage guide surface are more worn and seized. In addition to being prevented, abnormal wear of the column portion is further prevented.
  • a roller bearing including an inner ring, an outer ring, a plurality of rollers interposed between the inner ring and the outer ring, and a cage that holds the rollers.
  • the cage has an integrally formed cage body, and a first ring and a second ring fixed to the cage body, and the cage body has a first annular portion and a second annular portion. And a pillar portion that divides the two annular portions into pockets, the first ring is fixed to the first annular portion, and the second ring is fixed to the second annular portion.
  • a cage guide surface for guiding the cage in the radial direction is provided only on an inner periphery of the outer ring, and the guided surface guided by the cage guide surface is the cage.
  • the first ring and the second ring; Ring and the second ring is obtained by adopting the configuration that is formed in an annular shape of a material having a high modulus of elasticity than the material of each said retainer body.
  • the cage guide surface is provided on the inner circumference of the outer ring, and the guided surface is provided on the outer circumference of the cage, so that the PV value is the same as in the first invention. Suppression and lubricity are improved, and wear of the cage guide surface and the guided surface is prevented. Furthermore, since the first ring and the second ring, which are separate parts from the cage body, can be made of any material, the first ring and the second ring have a higher elastic modulus than the material of the cage body, respectively. It can be formed in an annular shape by a material having As a result, compared to the case where the cage is made of a single material, the first ring and the second ring improve the rigidity against deformation of the cage.
  • the guided surface and the cage guide surface can be contacted on both sides in the axial direction of the cage with the pocket as a boundary, the tilt of the cage can be suppressed well as in the first invention. Further, wear and seizure of the guided surface and the cage guide surface are further prevented, and abnormal wear of the column portion is further prevented.
  • the roller bearing according to the first invention suppresses the PV value between the guided surface of the cage and the cage guide surface of the outer ring even when the planetary rotating body provided in the planetary reduction gear is supported.
  • the lubricity of the guided surface of the cage and the cage guiding surface of the outer ring is improved, the slidability is improved on the guided surface of the cage, and the cage guiding surface and the guided surface are in contact with each other. Since it is possible to suppress the inclination of the cage, it is possible to prevent wear and seizure of the cage guide surface and the guided surface, which are cage guide portions, and to prevent abnormal wear of the cage pillars.
  • the roller bearing according to the second aspect of the present invention suppresses the PV value between the guided surface of the cage and the cage guide surface of the outer ring, even when supporting the planetary rotating body provided in the planetary reduction gear.
  • This improves the lubricity of the guided surface of the cage and the cage guiding surface of the outer ring, and further suppresses elliptical deformation and inclination of the cage when contacting the cage guiding surface and the guided surface. It is possible to prevent wear and seizure of the cage guide surface and the guided surface, which are the cage guide portions, and to prevent abnormal wear of the cage pillars.
  • Sectional drawing which shows the structure of the roller bearing which concerns on 1st embodiment of this invention.
  • Sectional drawing which shows the structure of a planetary reduction gear provided with the roller bearing which concerns on 1st embodiment.
  • Sectional drawing in the arrow line shown in FIG. Sectional drawing which shows the structure of the roller bearing which concerns on 2nd embodiment of this invention.
  • the side view which shows the structure of the roller bearing which concerns on 3rd embodiment of this invention.
  • Side view of the first ring according to the third embodiment Sectional drawing which shows the structure of the roller bearing which concerns on 4th embodiment of this invention.
  • Sectional drawing which shows the structure of the roller bearing which concerns on 5th embodiment of this invention.
  • the roller bearing shown in FIG. 1 includes an inner ring 1, an outer ring 2, a plurality of rollers 3 interposed between the inner ring 1 and the outer ring 2, and a cage 4 that holds these rollers 3.
  • the inner ring 1, the outer ring 2 and the cage 4 are set to the same central axis (bearing central axis indicated by a one-dot chain line in the drawing).
  • the inner ring 1 is an annular bearing part having a conical raceway surface 5, a small brim portion 6, and a large brim portion 7 on the outer periphery.
  • the outer ring 2 is an annular bearing part having a conical raceway surface 8 on the inner periphery and cage guide surfaces 9 and 10 for guiding the cage 4 in the radial direction.
  • the cage guide surfaces 9 and 10 are provided only on the inner periphery of the outer ring 2.
  • the cage guide surface 9 is formed on the inner diameter small diameter side of the inner circumference of the outer ring 2 with the raceway surface 8 as a boundary, and the cage guide surface 10 is formed on the opposite inner diameter large diameter side.
  • the cage guide surfaces 9 and 10 have a conical shape that forms the same surface as the raceway surface 8.
  • the roller 3 is a tapered roller that is in rolling contact with the raceway surface 5 of the inner ring 1 and the raceway surface 8 of the outer ring 2.
  • the single-row tapered roller bearing is exemplified, but an appropriate type of roller bearing such as a cylindrical roller bearing or a double-row roller bearing may be used.
  • the inner ring 1, the outer ring 2 and the roller 3 are usually made of steel.
  • Examples of the steel include high carbon chrome bearing steel and bare steel.
  • an inner ring assembly is constituted by the inner ring 1, the plurality of rollers 3 and the cage 4.
  • the retainer 4 includes a retainer body 11 that is integrally formed, and a first ring 12 and a second ring 13 that are attached to the outer periphery of the retainer body 11.
  • the retainer body 11 is formed with a first annular portion 14, a second annular portion 15, and a column portion 17 that divides the annular portions 14 and 15 into pockets 16.
  • the first annular portion 14 and the second annular portion 15 are continuous over the entire circumference in the circumferential direction.
  • the outer diameter of the second annular portion 15 is set larger than that of the first annular portion 14.
  • grooves for use in fixing the corresponding first ring 12 or second ring 13 are formed over the entire circumference in the circumferential direction.
  • the pocket 16 is a space for accommodating the rollers 3.
  • the column parts 17 exist at equal intervals in the circumferential direction.
  • the first ring 12 has a guided surface 18 that is guided in the radial direction by a cage guide surface 9 formed on the small inner diameter side of the outer ring 2.
  • the second ring 13 has a guided surface 19 that is guided in the radial direction by the cage guide surface 10 formed on the inner diameter / large diameter side of the outer ring 2.
  • Each of the first ring 12 and the second ring 13 has the illustrated cross-sectional shape over the entire circumference in the circumferential direction.
  • the first ring 12 and the second ring 13 are forcibly fitted in the grooves of the corresponding first annular portion 14 or second annular portion 15 in the respective inner peripheral portions.
  • the first ring 12 and the second ring 13 are positioned in the axial direction and the radial direction with respect to the corresponding first annular portion 14 or second annular portion 15.
  • the first ring 12 and the second ring 13 are prevented from rotating in the circumferential direction with respect to the corresponding first annular portion 14 or second annular portion 15.
  • This circumferential detent means may be performed by an appropriate means such as welding or an interference fit to the groove.
  • the first ring 12 and the second ring 13 are fixed to the outer periphery of the corresponding first annular portion 14 or the second annular portion 15 by the positioning and rotation prevention described above.
  • the guided surface 18 and the guided surface 19 exist on the outer periphery of the corresponding first ring 12 or second ring 13 over the entire circumference in the circumferential direction.
  • the guided surface 18 and the guided surface 19 are surfaces having an angle ⁇ 1 with respect to the axial direction on arbitrary virtual planes including the central axes of the cage 4 and the outer ring 2, respectively.
  • the axial width of each of the guided surface 18 and the guided surface 19 extends over the entire width of the corresponding first ring 12 or second ring 13.
  • the cage guide surface 9 and the cage guide surface 10 that are coplanar with the raceway surface 8 of the outer ring 2 are axially arranged on an arbitrary virtual plane including the central axis of the cage 4 and the outer ring 2, respectively.
  • the surface has an angle ⁇ 2.
  • the angle ⁇ 1 and the angle ⁇ 2 are set to the same angle. For this reason, the cage guide surface 9 and the guided surface 18 and the cage guide surface 10 and the guided surface 19 are parallel to each other on the above-described virtual plane, and are in surface contact with each other in a conical shape. It is possible.
  • the radial clearances between the guided surface 18 and the cage guide surface 9 and between the guided surface 19 and the cage guide surface 10 are set to the same value, and the guide between the cage 4 and the outer ring 2 is set. It corresponds to the clearance.
  • the contact between the roller 3 and the column portion 17 does not contribute to guiding the cage 4 in the radial direction.
  • the cage 4 includes a cage body 11, a first ring 12, and a second ring 13, and does not have a portion facing both sides defining the width of the outer ring 2 in the axial direction.
  • the roller bearing according to the first embodiment can be arranged in either a front combination or a back combination, and in either combination, it is possible to apply preload by arbitrarily using both side surfaces of the outer ring 2. .
  • the cage body 11 is made of steel.
  • the steel include cold or hot rolled steel, carbon steel for mechanical structure, stainless steel, nickel / chromium / molybdenum steel, and the like.
  • the cage body 11 is made of a steel plate having a thickness capable of forming a basic overall shape by pressing, and is formed by a general manufacturing method of a cage punching cage.
  • the aforementioned groove is formed by punching after the aforementioned pressing.
  • the manufacturing method of the cage main body 11 may employ an appropriate processing means such as pressing, milling, or molding depending on the shape and material of the cage main body 11.
  • the cage body 11 may be formed of resin or high-strength brass.
  • the rolling surface of the roller 3 usually contacts either of the column portions 17 located on both sides in the circumferential direction of the roller 3 while rolling on the raceway surfaces 5 and 8.
  • the normal contact portion in the column portion 17 is formed of a material that is as excellent in self-lubricity as possible. If the pillar part 17 is formed of resin or high-strength brass, the slidability of the normal contact part in the pillar part 17 can be improved.
  • the above-mentioned high-strength brass is an alloy obtained by adding 2.0% by mass or less of aluminum, 3.0% by mass or less of manganese, and 1.5% by mass or less of iron to brass of 55.0 to 60.5% by mass of copper. Say.
  • the resin examples include polyamide (PA), polyacetal (POM), polycarbonate (PC), polyethylene terephthalate (PET), polybutylene terephthalate (PBT), polyether ether ketone (PEEK), polyphenylene sulfide ( Engineering plastics or super engineering plastics such as PPS), polytetrafluoroethylene (PTFE), polysulfone (PSF), polyethersulfone (PES), polyimide (PI), polyetherimide (PEI), PA46 + GF, PA66 + GF, etc. Examples thereof include glass fiber reinforced resin.
  • the rolling surface of the roller 3 comes into contact with either of the column portions 17 positioned on both sides in the circumferential direction of the roller 3 while rolling on the raceway surfaces 5 and 8.
  • the contact portion of the column portion 17 with the roller 3 is made of a material having an excellent self-lubricity as much as possible. If the column part 17 is formed of resin or high-strength brass, the wear of the column part 17 due to normal contact can be prevented as compared with steel.
  • first ring 12 and the second ring 13 are each integrally formed of a resin material. Since the guided surface 18 and the guided surface 19 are each made of the resin material described above, they have a lower coefficient of friction than the surface of the steel cage body 11.
  • the resin material may be any material as long as it can form the guided surfaces 18 and 19 having a lower coefficient of friction than the surface of the cage body 11, and is preferably excellent in self-lubricity as much as possible.
  • resin materials having good self-lubricating properties include polyamide (PA), polyacetal (POM), polybutylene terephthalate (PBT), polyetheretherketone (PEEK), polytetrafluoroethylene (PTFE), and the like.
  • a sintered material containing a solid lubricant may be adopted as a material for forming the first ring 12 and the second ring 13.
  • This kind of sintered material also exhibits good self-lubricating properties. Therefore, the guided surfaces 18 and 19 made of the surface of this kind of sintered material have a lower coefficient of friction than the surface of the steel cage body 11.
  • Examples of the above-mentioned sintered material include those containing graphite.
  • graphite it is possible to obtain a sintered material excellent in self-lubricity by increasing the blending amount of graphite in the sintered material as graphite powder having high fluidity.
  • a sintered material for example, a raw material powder containing graphite powder and metal powder is molded in a mold and then sintered, and the granulated powder is used as the graphite powder and sintered.
  • the ratio of free graphite on the surface of the material is 25% to 80% in area ratio, the average particle size of the granulated powder is 60 ⁇ m to 500 ⁇ m, and the blending ratio of the granulated powder in the raw material powder is 3% to 15% by weight.
  • This sintered material is disclosed in Japanese Patent Laid-Open No. 2014-25527, and a detailed description thereof is omitted.
  • this planetary speed reducer includes a planetary rotating body 105 as a planetary gear meshing with both gears 102 and 104 between a sun gear 102 attached to the input shaft 101 and an internal gear 104 fixed to the housing 103.
  • each planetary rotator 105 is rotatably supported by the carrier 107 connected to the output shaft 106, and the planetary rotator 105 revolves while rotating between the sun gear 102 and the internal gear 104.
  • the revolving motion is output to the output shaft 106 via the carrier 107.
  • a pair of roller bearings 100 according to the first embodiment are disposed between the planetary rotating body 105 and the carrier 107 provided in the planetary reduction gear.
  • the outer ring 2 of each rolling bearing 100 is attached to the planetary rotator 105 and rotates integrally with the planetary rotator 105.
  • the inner ring 1 of each rolling bearing 100 is attached to a support shaft 108 provided on the carrier 107 and is stationary with respect to the outer ring 2.
  • the roller bearing 100 is given a preload for making the bearing internal clearance negative. Since the roller bearing 100 supports the planetary rotator 105 without play, the movement of the planetary rotator 105 is stabilized, and normal meshing between the planetary rotator 105 and the sun gear 102 or the internal gear 104 can be ensured. . In addition, although the back combination was illustrated as arrangement
  • the planetary speed reducer shown in the figure performs the first speed reduction of the final speed reducer provided inside the wheel rim of the super large dump truck.
  • the super large dump truck is intended for mines and has a load capacity of 300 t or more.
  • the inventors of the present application have examined the usage environment of the final ultra-high dump final reduction gear.
  • the roller bearing 100 revolving around the sun gear 102 has a revolving diameter of about 500 mm and a revolving speed of about 500 rpm.
  • the rotation speed was about 1300 rpm, and the maximum centrifugal acceleration was about 75G. When such strong centrifugal acceleration is applied, the lubricating oil inside the bearing becomes dilute in the load region, and the tendency to deviate to the opposite side in the circumferential direction from the load region is remarkable.
  • the roller bearing according to the first embodiment is provided with cage guide surfaces 9 and 10 on the inner circumference of the outer ring 2 and guided surfaces 18 and 19 on the outer circumference of the cage 2. Therefore, as shown in FIGS. 2 and 3, in the support application of the planetary rotating body 105 provided in the planetary speed reducer, the cage 4 is guided in the radial direction by the inner circumference of the outer ring 2 that rotates integrally with the planetary rotating body 105. Is done. For this reason, compared with the case where the cage 4 is guided by the inner ring 1, between the guided surface 18 and the cage guiding surface 9 and between the guided surface 19 and the cage guiding surface 10 shown in FIG. 1.
  • the relative speed difference (V) between them becomes small, and the circumferential lengths of the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 become long and the contact surface pressure (P) becomes low.
  • the lubricating oil moves to the inner peripheral side of the outer ring 2 by the action of a large centrifugal force accompanying the revolution movement of the planetary rotating body 105. 1 is easily supplied to the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 shown in FIG. 1, and the lubricity of the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 is improved. Due to the suppression of the PV value and the lubricity, wear and seizure of the guided surfaces 18 and 19 and the cage guide surfaces 9 and 10 are prevented.
  • the guided surface 18 of the first ring 12 and the guided surface 19 of the second ring 13, which are separate parts fixed to the cage body 11, are on the surface of the cage body 11. Since the friction coefficient is lower than that of the guide surfaces 18, 19, the cage guide surfaces 9, 10 and the guided surfaces 18, 19 are further prevented from being worn and seized. By preventing the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 from being worn, it is possible to prevent the guide 4 from rolling and guide the rolling element 4 and prevent the column portion 17 from wearing abnormally. Also become.
  • the roller bearing according to the first embodiment includes the contact between the guided surface 18 and the cage guiding surface 9 on both sides in the axial direction of the cage 4 with the pocket 16 as a boundary, and the guided surface 19 and the cage guiding surface. 10 can be contacted, so that the tilt of the cage 4 can be suppressed even when a large centrifugal force due to the revolving motion of the planetary rotating body 105 shown in FIGS. 2 and 3 acts on the cage 4.
  • a decrease in the contact area between the guided surface 18 and the cage guide surface 9 and a decrease in the contact area between the guided surface 19 and the cage guide surface 10 can be suppressed, and an abnormality between the column portion 17 and 3. Therefore, wear and seizure of the guided surfaces 18 and 19 and the cage guide surfaces 9 and 10 are further prevented, and abnormal wear of the column portion 17 is further prevented.
  • the roller bearing according to the first embodiment even when supporting the planetary rotating body 105 provided in the planetary reduction gear, the guided surface of the cage 4 shown in FIG. 1. 18 and 19 and the cage guide surfaces 9 and 10 of the outer ring 2 are suppressed, and the lubricity of the guided surfaces 18 and 19 of the cage 4 and the cage guide surfaces 9 and 10 of the outer ring 2 is improved.
  • the guided surfaces 18 and 19 and the cage guiding surfaces 9 and 10 are parallel to each other on a virtual plane including the central axis of the cage 4 and the outer ring 2 arranged coaxially. Since it has a surface shape, it is possible to prevent wear by making the contact mode between the guided surface 18 and the cage guide surface 9 and the contact mode between the guided surface 19 and the cage guide surface 10 into a surface contact.
  • the first ring 12 and the second ring 13 are each formed of a resin material or a sintered material containing graphite. Can have a self-lubricating property.
  • the first ring 12 and the second ring 13 are present only in a region opposed to the inner circumference of the outer ring 2 in the radial direction. Can be replaced with existing roller bearings.
  • the raceway surface 8 of the outer ring 2 and the cage guide surfaces 9 and 10 are the same surface, but the raceway surface 8 and the cage guide surface may be different surfaces.
  • the first ring 12 and the second ring 13 are each formed of a single material and the entire ring has a lower coefficient of friction than the surface of the cage body 11, but at least the guided surface 18, It is only necessary to use a low friction coefficient in the portion 19 and the portion to be the guided surface of the ring and the remaining annular portion may be formed of different materials, and the ring portion may improve the mechanical strength of the ring.
  • FIG. 4 shows a second embodiment as an example. In the following, only differences from the first embodiment will be described.
  • the roller bearing according to the second embodiment is formed with cylindrical retainer guide surfaces 21 and 22 on the inner periphery of the outer ring 20, and the first ring 31 and the second ring 32 of the retainer 30.
  • Cylindrical guided surfaces 33 and 34 are formed. These cylindrical surface central axes coincide with the central axis of the outer ring 20 and the central axis of the cage 30.
  • the guided surfaces 33 and 34 and the cage guide surfaces 21 and 22 do not have an angle with respect to the axial direction on a virtual plane including the central axis of the cage 30 and the outer ring 20 arranged coaxially. For this reason, when the guided surfaces 33 and 34 and the corresponding cage guide surface 21 or the cage guide surface 22 come into contact with each other in the direction of the centrifugal force, no axial component force is generated, and the cage 30 is reliably Guided.
  • the first ring 31 and the second ring 32 have ring bodies 35 and 36 each formed in an annular shape from steel.
  • the ring body portion 35 and the ring body portion 36 have a cylindrical inner surface and an outer surface, respectively.
  • the guided surface 33 and the guided surface 34 are each composed of a surface treatment layer fixed so as to cover the outer peripheral surface of the corresponding ring body portion 35 or the ring body portion 36.
  • This surface treatment is for improving the slidability of the guided surfaces 33 and 34 as compared with the surfaces of the ring bodies 35 and 36 and the surface of the cage main body 37, and preferably has excellent self-lubricity as much as possible.
  • the surface treatment one having a lower friction coefficient than the surface of the cage body 37 is particularly preferable, and examples thereof include fluorine resin coating, molybdenum coating, DLC coating, ceramic coating, and hard chrome plating.
  • the thickness of the surface treatment layer forming the guided surfaces 33 and 34 is exaggerated.
  • a substantially entire area in the radial direction of the first ring 31 and the second ring 32 is constituted by the corresponding ring body portion 35 or the ring body portion 36.
  • the mechanical strength of each of the first ring 31 and the second ring 32 is substantially set by the corresponding ring body portion 35 or the ring body portion 36.
  • the cage body 37 is made of resin or high-strength brass. For this reason, when the pillar part of the cage body 37 abnormally contacts the roller 3, the aggressiveness of the cage body 37 against the roller 3 is lower than that of the same-shaped cage body made of steel. Instead, the rigidity with respect to the deformation of the cage body 37 is inferior to that of the same shape cage body made of steel.
  • the elastic modulus of steel which is the material forming the ring body portion 35 of the first ring 31 and the ring body portion 36 of the second ring 32, is compared to the resin material or sintered material that is the material forming the cage body 37. Is expensive. That is, the first ring 31 and the second ring 32 are formed in an annular shape from a material having a higher elastic modulus than the material of the cage body 37 in the corresponding ring body part 35 or ring body part 36, respectively. For this reason, compared with the case where the cage having the same shape as the cage 30 is formed only from the material of the cage body 37, the rigidity against deformation of the cage 30 is improved by the first ring 31 and the second ring 32. ing.
  • Centrifugal force due to the revolving motion of the planetary rotating body acts on the cage 30, the guided surface 33 of the first ring 31 contacts the cage guiding surface 21 of the outer ring 20, and the guided surface 34 of the second ring 32
  • the cage 30 undergoes elliptical deformation such that its diameter decreases in the direction in which the centrifugal force acts.
  • a pocket in which the pocket clearance is reduced is generated in the cage body 37 that is elliptically deformed.
  • the rigidity with respect to the deformation of the cage 30 is improved by the first ring 31 and the second ring 32, so that the above-described elliptical deformation is suppressed, and as a result, the cage body 37 Abnormal wear of the column is prevented.
  • the roller bearing according to the second embodiment has a PV value between the guided surfaces 33 and 34 of the cage 30 and the cage guide surfaces 21 and 22 of the outer ring 20 even when the planetary rotor is supported.
  • the cage guide surface 21 is further improved than in the first embodiment. , 22 and guided surfaces 33, 34 can be prevented from being worn and seized, and abnormal wear of the column portion of the cage 30 can be prevented.
  • the first ring 31 and the second ring 32 have ring bodies 35 and 36 each formed in an annular shape by steel, and the guided surfaces 33 and 34 are the rings. Since it consists of a surface treatment layer applied to the body portions 35 and 36, the first ring 31 and the second ring 32 improve the rigidity against the elliptical deformation of the cage 30, and excellent sliding on the guided surfaces 33 and 34. Can have sex.
  • the guided surface is provided over the entire outer periphery of the first ring and the second ring, but the guided surface may be provided intermittently in the circumferential direction.
  • FIG. 5 shows a roller bearing according to a third embodiment.
  • FIG. 5 shows a side surface of the roller bearing according to the third embodiment on the first ring 42 side, but the above-described gap width change in the second ring 43 is common to the first ring 42.
  • FIG. 5 shows a side surface of the roller bearing according to the third embodiment on the first ring 42 side, but the above-described gap width change in the second ring 43 is common to the first ring 42.
  • the first ring 42 has protrusions 44 protruding in the radial direction at equal intervals in the circumferential direction.
  • the guided surface 45 is provided at the distal end of the protruding portion 44 in the radial direction.
  • the outer peripheral portion between the protrusions 44 adjacent in the circumferential direction is an intermediate surface 46 having an outer diameter smaller than the guided surface 45 over the entire axial width of the first ring 42. ing. Therefore, as shown in FIG. 5, the radial width of the gap g set between the intermediate surface 46 and the inner periphery of the outer ring 2 is set between the guided surface 45 and the inner periphery of the outer ring 2. It becomes larger than the guide clearance.
  • the lubricating oil is less likely to enter the above-described guide gap, and more easily enters the gap g. That is, the oil permeability that crosses between the outer periphery of the first ring 42 and the inner periphery of the outer ring 2 in the axial direction is improved by the gap g.
  • the pitch in the circumferential direction of the protrusions 44 and the pitch in the circumferential direction of the rollers 3 by the cage 40 are the same. That is, the protrusion 44 exists only in the circumferential range facing the end surface of the roller 3 in the axial direction.
  • the space between the rollers 3 adjacent in the circumferential direction inside the bearing is opened from the gap g in the axial direction toward the outside of the bearing.
  • the opening area is not reduced by the protrusion 44 because the protrusion 44 does not protrude in the circumferential direction with respect to the end face of the roller 3. For this reason, the protrusion part 44 does not prevent the lubricating oil from flowing into the space between the rollers 3 described above.
  • the roller bearing according to the third embodiment has the protruding portions 44 that the first ring 42 and the second ring 43 protrude in the radial direction at circumferential intervals corresponding to the rollers 3, respectively. Since the surface 45 is provided on the protrusion 44, the protrusion 44 prevents the inflow of lubricating oil into the space between the rollers 3 adjacent in the circumferential direction by the gap g between the protrusions 44 adjacent in the circumferential direction. The oil permeability between each of the first ring 42 and the second ring 43 and the inner periphery of the outer ring 2 can be improved.
  • the roller bearing according to the fourth embodiment is different from the roller bearing according to the first to third embodiments in that the bearing type is changed from a tapered roller bearing to a cylindrical roller bearing.
  • the outer ring 50 has collars 51 and 52 on both sides in the axial direction.
  • the cage guide surfaces 53 and 54 are formed in cylindrical shapes on the inner circumferences of the corresponding collars 51 and 52, respectively.
  • the cage guide surfaces 53 and 54 have the same diameter.
  • the first annular portion 61 and the second annular portion 62 of the cage main body 60 have the same shape, and the first ring 63 and the second ring 64 have the same shape.
  • the guided surface 65 formed on the first ring 63 and the guided surface 66 formed on the second ring 64 are along the axial direction (angle 0 ° with respect to the axial direction) on the above-described virtual plane. For this reason, the guided surfaces 65 and 66 and the cage guide surfaces 53 and 54 are parallel to each other on the above-described virtual plane.
  • the roller bearing according to the fifth embodiment is different from the roller bearing according to the first to third embodiments in that the bearing type is changed from a tapered roller bearing to a self-aligning roller bearing.
  • the outer ring 70 has a spherical track 71 corresponding to the spherical rollers 81 and 82 on the inner periphery.
  • the cage main body 90 has a pair of first annular portions 91 that define the cage width, and a second annular portion 92 that is positioned at the center of the cage width. A space between each of the first annular portions 91 and 91 and the second annular portion 92 is divided into pockets by a pillar portion 93.
  • a first ring 94 is fixed to each of the first annular portions 91, 91, and a second ring 95 having an outer diameter larger than that of the first ring 94 is fixed to the second annular portion 92.
  • cage guide surfaces 72, 72 for guiding the guided surface 96 formed on the first ring 94 are formed on the inner periphery of the spherical track 71 extending in the axial direction.
  • the axial center portion of the spherical track 71 that does not contact the double-row spherical rollers 81 and 82 is a cage guide surface 73 that guides a guided surface 97 formed on the second ring 95.
  • the guided surface 96 is along a cage guide surface 72 that is flush with the spherical track 71 on the virtual plane, and the guided surface 97 is included in the spherical track 71 on the virtual plane.
  • the guided surfaces 96 and 97 and the cage guide surfaces 72 and 73 are parallel to each other on the above-described virtual plane.

Abstract

La présente invention concerne la prévention de l'usure et du blocage de la partie de guidage d'un support, ainsi que l'usure anormale d'une partie en forme de colonne du support, même lorsqu'un élément rotatif planétaire prévu sur un réducteur à engrenage planétaire est supporté par des paliers à roulement. Des surfaces de guidage (9, 10) de support sont prévues sur la périphérie interne d'une voie externe (2). La présente invention comporte une première bague (12) ancrée sur une première partie annulaire (14) d'un corps de support (11) et une seconde bague (13) ancrée sur une seconde partie annulaire (15) du corps de support (11). La première bague (12) et la seconde bague (13) comprennent des surfaces guidées (18, 19) qui ont un coefficient de friction inférieur à celui de la surface du corps de support (11). La première bague (12) et la seconde bague (13) sont formées en des configurations annulaires à partir d'un matériau ayant un module d'élasticité supérieur à celui du matériau du corps de support (11).
PCT/JP2016/088171 2015-12-24 2016-12-21 Palier à roulement WO2017110905A1 (fr)

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JP2015251798A JP2017115977A (ja) 2015-12-24 2015-12-24 ころ軸受
JP2015-251798 2015-12-24

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Publication number Priority date Publication date Assignee Title
JP7135818B2 (ja) * 2018-12-12 2022-09-13 株式会社ジェイテクト 転がり軸受装置
JP7247598B2 (ja) * 2019-01-21 2023-03-29 株式会社ジェイテクト 転がり軸受装置
CN112610595A (zh) * 2020-12-24 2021-04-06 中国航发哈尔滨轴承有限公司 带有滚动摩擦组件的滚动轴承

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4941233B1 (fr) * 1970-12-28 1974-11-07
JP2015083861A (ja) * 2013-10-25 2015-04-30 日本精工株式会社 針状ころ軸受用保持器及び針状ころ軸受

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4941233B1 (fr) * 1970-12-28 1974-11-07
JP2015083861A (ja) * 2013-10-25 2015-04-30 日本精工株式会社 針状ころ軸受用保持器及び針状ころ軸受

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