[go: up one dir, main page]

WO2011155456A1 - Roulement à billes à gorge profonde - Google Patents

Roulement à billes à gorge profonde Download PDF

Info

Publication number
WO2011155456A1
WO2011155456A1 PCT/JP2011/062959 JP2011062959W WO2011155456A1 WO 2011155456 A1 WO2011155456 A1 WO 2011155456A1 JP 2011062959 W JP2011062959 W JP 2011062959W WO 2011155456 A1 WO2011155456 A1 WO 2011155456A1
Authority
WO
WIPO (PCT)
Prior art keywords
ball
shoulder
outer ring
inner ring
raceway groove
Prior art date
Application number
PCT/JP2011/062959
Other languages
English (en)
Japanese (ja)
Inventor
上野　崇
Original Assignee
Ntn株式会社
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 Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2011155456A1 publication Critical patent/WO2011155456A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3862—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together
    • F16C33/3875—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together made from plastic, e.g. two injection moulded parts joined by a snap fit
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/62—Selection of substances
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C2208/52—Polyphenylene sulphide [PPS]
    • 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
    • F16C2208/60—Polyamides [PA]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/06—Temperature
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/90—Surface areas
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Definitions

  • This invention relates to a deep groove ball bearing in which a ball is incorporated between an outer ring and an inner ring and the ball is held by a cage.
  • the rotation of the final drive gear 1 of the transmission is transmitted from the final driven gear 2 to the differential case 3 that supports the gear 2, and the rotation of the differential case 3 is transmitted from a pair of pinions 5 fixed to the pinion shaft 4.
  • the cylindrical portions 8a formed at both ends of the differential case 3, 8b is rotatably supported by a pair of bearings B supported by the housing 9.
  • both radial load and thrust load can be supported as a bearing that supports a shaft provided with the helical gear. It is necessary to use a bearing.
  • the tapered roller bearing since the tapered roller bearing has a large load capacity and can receive both a thrust load and a radial load, it is suitable for a bearing for supporting the differential case 3 and a bearing for supporting a transmission shaft.
  • the roller bearing In the roller bearing, there is a problem that torque loss is large and fuel consumption is increased.
  • the deep groove ball bearing has a smaller load capacity than a tapered roller bearing. Therefore, when the rolling fatigue life is requested to be the same as or comparable to that of a tapered roller bearing, a decrease in the rolling fatigue life is a problem. Become.
  • An object of the present invention is to provide a deep groove ball bearing that can completely prevent a ball from climbing over a shoulder even under a large thrust load and has a long life against rolling fatigue life.
  • the height of the shoulder on one side and the shoulder on the other side of the inner ring raceway groove is higher than the height of the shoulder on the other side of the outer ring raceway groove and one side of the inner ring raceway groove.
  • the shoulder height H 1 of the outer ring with respect to the ball diameter d is The ratio H 1 / d is in the range of 0.28 to 0.50, and the shoulder of the inner ring with respect to the ball diameter d.
  • the ratio H 2 / d of the height H 2 is in the range of 0.37 to 0.50, and at least the outer ring and the inner ring among the outer ring, the inner ring and the ball are in a weight ratio of 0.8 to 1.2% carbon.
  • the ratio H 1 / d of the shoulder height H 1 to the ball diameter d is 0.28 or more. This is based on the results of the test.
  • the ratio H 2 / d of the shoulder height H 2 to the ball diameter d is set to 0.37 or more. This is also a rule based on the test results.
  • At least the outer ring and the inner ring are carbonitrided with high carbon bearing steel with a large amount of carbon, quenched from a high temperature, and then tempered at a relatively low temperature. Since the amount of retained austenite in the surface layer portion is 15 to 20%, the rolling fatigue life can be remarkably improved.
  • the height of the shoulder on one side and the shoulder on the other side of the inner ring raceway groove is higher than the height of the shoulder on the other side of the outer ring raceway groove and one side of the inner ring raceway groove.
  • the shoulder height H 1 of the outer ring with respect to the ball diameter d is The ratio H 1 / d is in the range of 0.28 to 0.50, and the shoulder of the inner ring with respect to the ball diameter d.
  • the ratio H 2 / d of the height H 2 is in the range of 0.37 to 0.50, and at least the outer ring and the inner ring of the outer ring, the inner ring and the ball are in a weight ratio of 0.6 to 1.2% carbon.
  • the ratio H 1 / d of the shoulder height H 1 of the outer ring to the ball diameter d is set to 0, as in the deep groove ball bearing according to the first invention.
  • the ratio H 2 / d of the shoulder height H 2 of the inner ring to the ball diameter d of the ball is 0.37 or more, so that it is possible to completely prevent the ball from riding on the shoulder.
  • the outer ring and the inner ring contain 0.6 to 1.2% carbon, 0.15 to 1.1% silicon, 2.0% or less chromium, and 0.3 to 1.5% manganese in terms of weight ratio.
  • formed by bearing steel again the bearing steel was carbonitrided at a carbonitriding processing temperature in excess of a 1 transformation point, cooled to a temperature below the a 1 transformation point, then the quenching temperature range of 790 ⁇ 830 ° C.
  • an austenite crystal grain having an average grain size of 8 ⁇ m or less can be obtained, has a long life against rolling fatigue, improves crack strength, and decreases the aging rate. be able to.
  • the radius of curvature of the raceway groove of the outer ring is r 1
  • the radius of curvature of the raceway groove of the inner ring is r 2
  • the ball diameter of the ball is d
  • the shoulder height of the outer ring with respect to the ball diameter d It is in the range of the ratio H 3 / d of 0.08 to 0.25 of H 3, and the ratio H 4 / d of 0.08 to 0.25 of the inner ring shoulder height H 4 for the spherical diameter d of the ball. If the above-mentioned range is set, the shoulders facing each other in the radial direction of the outer ring and the inner ring should have a larger distance than the case where each of the above shoulders has the same height as that of the standard deep groove ball bearing. Therefore, a cage having a large radial width and a high strength can be adopted as the cage.
  • the cage includes a cylindrical first divided cage made of a synthetic resin molded product and a synthetic resin cylindrical second divided cage inserted inside the first divided cage. And a notch for forming a circular pocket for holding a ball in a state where both the split cages are combined inside and outside on one axial side surface of the first split cage and the other axial side surface of the second split cage.
  • a connecting means is provided that is spaced apart in the circumferential direction, and in which the first divided holder and the second divided holder form a circular pocket, and the two divided holders are not separated in the axial direction. What consists of composition can be adopted.
  • Assembling the cage having the above-described configuration is as follows. After the ball is assembled between the outer ring and the inner ring, the first divided cage is formed in the bearing from one side of the outer ring and the inner ring. The second split cage is inserted into the bearing from the other side between the outer ring and the inner ring, and the ball is inserted into the notch formed in the second split cage. Is inserted so that the other side portion in the axial direction of the second split cage is fitted in the one side portion in the axial direction of the first split cage, and both split cages are connected by the connecting means. Link.
  • the connecting means are engaged with each other so that the first divided cage and the second divided cage are not separated in the axial direction. Therefore, the deep groove ball bearing can be easily assembled.
  • first split cage and the second split cage having different diameters are asymmetrical combinations in which both end portions are shifted in the axial direction (left-right direction), and the rear end portion in the insertion direction when assembled is the shoulder of the outer ring and the inner ring Therefore, the first split holder and the second split holder can be securely assembled without interfering with the shoulders of the inner and outer rings.
  • an inward engagement claw is provided at a tip portion of a pillar portion formed between adjacent notch portions of the first split cage, and between the adjacent notch portions of the second split cage.
  • An outward engaging claw is provided at the tip of the formed column part, and the engaging claw of the first divided holder is engaged with an engaging recess formed on the outer diameter surface of the second divided holder. It is possible to employ a configuration in which the engaging claw of the two-divided cage is engaged with an engaging recess formed on the inner diameter surface of the first divided cage.
  • the cutout portion has a circular shape exceeding a half circle in a planar shape, and has a pair of opposed pocket claws at the opening end, and a spherical shape whose cross-sectional shape follows the outer periphery of the ball It may be formed into a shape, or may be formed into a plane U shape that forms a cylindrical pocket in the fitted state of the first divided holder and the second divided holder.
  • the split cage is effectively prevented from falling off by engaging the engaging claw and the engaging recess and engaging the pocket claw and the ball. can do.
  • the ball does not interfere with the assembly of the cage, and the cage can be easily incorporated into the bearing.
  • the circumferential clearance formed between the engaging claw and the engaging recess is larger than the circumferential pocket clearance formed between the ball and the pocket.
  • first split cage and the second split cage can be obtained by setting the axial clearance formed between the engaging claw and the engaging recess larger than the axial pocket clearance formed between the ball and the pocket.
  • the inner surfaces of the pair of opposing pocket claws abut against the outer peripheral surface of the ball, and the engaging claws abut against the axial end surface of the engaging recess. The effect of preventing damage to the engaging claws can be obtained.
  • a circumferential clearance formed between the engaging claw and the engaging recess is accommodated in a pocket formed by two notches that are opposed in the radial direction and in the pocket.
  • the first split cage and the second split cage are formed of a synthetic resin excellent in oil resistance.
  • a resin include polyamide 46 (PA46), polyamide 66 (PA66), and polyphenylene sulfide (PPS).
  • PA46 polyamide 46
  • PA66 polyamide 66
  • PPS polyphenylene sulfide
  • PPS polyphenylene sulfide
  • PPS polyphenylene sulfide
  • PA66 polyamide 66
  • the cage is not limited to the one having the above-described configuration, for example, a cage that is divided into two in the axial direction.
  • Each of the cages has a plurality of hemispherical pocket portions and a width of the pocket portion.
  • a plurality of coupling plate portions having the same width as the dimensions are continuously waved in the circumferential direction, the outer diameters of the coupling plate portions of the two waveform split cages are the same, and one waveform
  • the position of the pocket part of the split cage is shifted to the inner diameter side with respect to the coupling plate part, and the position of the pocket part of the other waveform split cage is shifted to the outer diameter side with respect to the coupling plate part.
  • both the first invention and the second invention can completely prevent the balls from climbing over the shoulder even when subjected to a large thrust load, and have a long life against rolling fatigue life.
  • a deep groove ball bearing can be obtained.
  • it can be incorporated into a bearing device where a tapered roller bearing is required, and the incorporation into the bearing device can reduce torque loss and achieve low fuel consumption.
  • the outer ring and the inner ring are formed of high carbon bearing steel with a large amount of carbon, and after carbonitriding the high carbon bearing steel and quenching from high temperature, By tempering at a low temperature, the amount of retained austenite in the surface layer portion is 15 to 20%, so that the rolling fatigue life can be remarkably improved.
  • the deep groove ball bearing according to the second invention to form a outer ring and the inner ring carbon intensive bearing steel, after the bearing steel was carbonitrided at a carbonitriding processing temperature above the A 1 transformation point, cooled to a temperature below the a 1 transformation point, then, by a heat treatment of performing quenching and re-heating in the quenching temperature range of 790 ⁇ 830 ° C., to form the austenite crystal grains of 8 ⁇ m following microstructure with an average grain size Therefore, it is possible to obtain a deep groove ball bearing that has a long life against rolling fatigue, an improved crack strength, and a low durability with a low rate of aging.
  • FIG. 5 is a plan view of the first split cage shown in FIG. Top view showing the pocket clearance in the axial direction with the ball in the pocket Partial plan view showing another example of a synthetic resin cage
  • retainer The top view of the part which shows the further another example of a holder
  • a ball 31 is incorporated between a raceway groove 12 formed on the inner diameter surface of the outer ring 11 and a raceway groove 22 provided on the outer diameter surface of the inner ring 21. Is held by the cage 40.
  • the height of the shoulder 13a located on one side of the raceway groove 12 is higher than the shoulder 13b located on the other side.
  • the height of the shoulder 23b located on the other side of the raceway groove 22 is higher than the height of the shoulder 23a located on one side. It is high.
  • the high shoulders 13a and 23b are referred to as thrust load side shoulders 13a and 23b, and the low shoulders 13b and 23a are referred to as thrust non-load side shoulders 13b and 23a.
  • the height of the shoulder 13a on the thrust load side of the outer ring 11 is H 1
  • the height of the shoulder 23b on the thrust load side of the inner ring 21 is H 2
  • the ball diameter of the ball 31 is d
  • the ball diameter d of the ball 31 The ratio H 1 / d of the shoulder height H 1 of the outer ring 11 is in the range of 0.28 to 0.50
  • the ratio of the shoulder height H 2 of the inner ring 21 to the ball diameter d of the ball 31 is H 2 / d is in the range of 0.37 to 0.50.
  • the height H 3 of the shoulder 13b on the thrust non-load side of the outer ring 11 and the height H 4 of the shoulder 23a on the thrust non-load side of the inner ring 21 are the same as the shoulder height of the standard deep groove ball bearing.
  • the standard deep groove ball bearing is a bearing in which the height of the pair of shoulders of the outer ring and the height of the pair of shoulders of the inner ring are the same.
  • the outer ring 11 and the inner ring 21 are, by weight ratio, carbon (C) 0.8 to 1.2%, silicon (Si) 0.4 to 1.0%, chromium (Cr) 0.2 to 1.2%. And a heat-treated product made of a high carbon bearing steel containing 0.8 to 1.5% of manganese (Mn).
  • quenching is performed from 830 to 870 ° C. to obtain a quenching termination temperature of 90 to 120 ° C., and then tempering in the range of 160 to 190 ° C. Is 25 to 50%, and the austenite content of the core is 15 to 20%.
  • the reason why the composition of the above-mentioned high carbon bearing steel is set to a high carbon of C 0.8 to 1.2% is that the surface layer portion is basically hardened by quenching and tempering. If Cr is less than 0.2%, carbide is not formed if the Cr is less than 0.2%, and the hardness of the surface layer is insufficient. If it exceeds 1.2%, the carbide becomes coarse and becomes a starting point of peeling. This is because the life is likely to be short.
  • Si stably increases the retained austenite of the surface layer to 25% or more, imparts temper softening resistance, and secures heat resistance, but 0.4% or more is necessary, but if Si exceeds 1% This is because, during the carbonitriding process, the enrichment of nitrogen and carbon from the skin to the surface layer is inhibited.
  • Mn is for securing the hardenability and quenching to the core, but increases the retained austenite in the surface layer with an element that stabilizes the retained austenite in the quenching and tempering processes. Addition of a large amount of Mn causes a decrease in cold workability and causes cracking and embrittlement, and therefore increases to a range not exceeding 1.5% Mn.
  • SUJ3 steel can be used as such a high carbon bearing steel. Mo is appropriately added to 0.3% for improving hardenability. SUJ5 steel is used as a material to which Mo is added.
  • the nitrogen content of the surface layer portion becomes high, and the Ms point of the surface layer portion decreases as compared with the core portion. Then, untransformed austenite is increased in the surface layer portion than in the core portion. Since nitrogen is high in the surface layer portion and the quenching start temperature (austenitizing temperature) is increased to 830 to 870 ° C., the retained austenite in the surface layer portion can be easily increased to 25% or more. In order to stably increase the retained austenite, the quenching end temperature is increased to about 100 ° C., preferably 90 to 120 ° C. In this quenching process, the martensitic transformation of the surface portion enriched with nitrogen starts later than the inside, and the amount of transformation is less than the inside, so that residual compressive stress is formed in the surface portion.
  • the quenching start temperature (austenitizing temperature) is 830 to 870 ° C., which is higher than that of ordinary quenching and tempering steel, the crack sensitivity value associated with quenching increases. Therefore, it is preferable to control the cooling rate in the martensitic transformation process by setting the cooling capacity H in the range of 300 to 150 ° C. in the quenching process to 0.2 cm ⁇ 1 or less.
  • carbonitriding is usually performed in a high-temperature gas in which ammonia is added to a carburizing or reducing gas.
  • the above conditions are immediately applied after carbonitriding in a temperature range of 830 to 870 ° C. Quench in oil.
  • the tempering temperature after quenching is set to a relatively low temperature of 160 to 190 ° C.
  • the retained austenite in the surface layer portion is set to a range of 25 to 50% by suppressing decomposition of the retained austenite in the tempering process.
  • the higher the retained austenite in this range the rolling fatigue life is improved under the lubrication conditions under the presence of foreign matter.
  • the surface hardness is lowered and the wear resistance is lowered. A range of 25 to 30% is preferable.
  • the core portion is tempered at a low temperature of 190 ° C. or lower, usually about 15 to 20% of retained austenite remains.
  • the ball 31 may be a heat-treated product similar to the outer ring 11 and the inner ring 21.
  • the holder 40 includes a first divided holder 41 and a second divided holder 42 inserted inside the first divided holder 41.
  • the first split holder 41 has a pair of opposed pocket claws 44 formed on the one side surface in the axial direction of the annular body 43 at equal intervals in the circumferential direction.
  • the planar shape of the annular body 43 is made of a synthetic resin molded product provided with a notch 45 having a size exceeding a half circle.
  • the inner diameter of the annular body 43 is substantially equal to the pitch circle diameter (PCD) of the balls 31, and the outer diameter is equal to the inner diameter of the shoulder 13a where the height of the outer ring 11 is high and the shoulder whose height is low.
  • the inner diameter of the outer ring 11 can be inserted into the bearing from the lower shoulder 13b side.
  • the inner surface of the notch 45 is a spherical shape along the outer periphery of the ball 31.
  • the first split holder 41 has a pair of opposed pocket claws 49 formed on the other side surface in the axial direction of the annular body 48 at equal intervals in the circumferential direction, and the annular body 48 is wound between each pair of opposed pocket claws 49. It consists of a molded product of synthetic resin provided with a cutout portion 50 having a size that exceeds a half of a half of the planar shape to be extracted.
  • the outer diameter of the annular body 48 is substantially equal to the pitch circle diameter (PCD) of the balls 31, and the inner diameter is the outer diameter of the high shoulder 23b of the inner ring 21 and the low shoulder 23a.
  • the outer diameter is within the range.
  • the second split cage 42 can be inserted into the bearing from the low shoulder 23a side, and can be fitted inside the first split cage 41.
  • the inner surface of the notch 50 is formed in a spherical shape along the outer periphery of the ball 31.
  • the shaft of the second split holder 42 is located between the first split holder 41 and the second split holder 42 within one side in the axial direction of the first split holder 41.
  • the first split holder 41 and the second split holder 42 are non-separated in the axial direction.
  • Means X are provided.
  • the connecting means X is provided with an inward engagement claw 46 at the tip of a pillar portion 43a formed between adjacent cutout portions 45 of the first split holder 41, and the engagement member X is provided on the inner diameter surface of the annular body 43.
  • a groove-like engagement recess 47 is formed on the same axis as the joint claw 46, and an outward engagement claw 51 is formed at the tip of a column part 48 a formed between the adjacent notches 50 of the second split holder 42.
  • an engagement recess 52 is formed on the outer diameter surface of the annular body 48 on the same axis as the engagement claw 51, and the engagement claw 46 of the first divided holder 41 and the second divided holder 42 are By the engagement of the engagement recess 52 and the engagement of the engagement claw 51 of the second split retainer 42 and the engagement recess 47 of the first split retainer 41, the first split retainer 41 and the second split retainer. 42 is not separated in the axial direction.
  • a synthetic resin excellent in oil resistance is used.
  • a synthetic resin include polyamide 46 (PA46), polyamide 66 (PA66), and polyphenylene sulfide (PPS). These resins may be selected and used according to the type of lubricating oil.
  • the deep groove ball bearing shown in the embodiment has the above-described structure.
  • the inner ring 21 is inserted inside the outer ring 11, the race groove 22 of the inner ring 21 and the race groove of the outer ring 11.
  • a required number of balls 31 are assembled between 12.
  • the inner ring 21 is offset in the radial direction with respect to the outer ring 11, a part of the outer diameter surface of the inner ring 21 is brought into contact with a part of the inner diameter surface of the outer ring 11, and 180 degrees in the circumferential direction from the contact part.
  • a crescent-shaped space is formed at a shifted position, and the ball 31 is assembled from one side of the space.
  • the ratio H 1 / d of the outer ring shoulder height H 1 to the ball diameter d of the ball 31 and the ratio H 2 / d of the inner ring shoulder height H 2 do not exceed 0.50. Because of the height, the ball 31 can be reliably assembled between the outer ring 11 and the inner ring 21.
  • the center of the inner ring 21 is made to coincide with the center of the outer ring 11, the balls 31 are arranged at equal intervals in the circumferential direction, and the outer ring 11 and the inner ring 21 from one side of the shoulder 13b where the height of the outer ring 11 is low.
  • the first split holder 41 is inserted between the notches 45 formed in the first split holder 41 so that the balls 31 are fitted therebetween.
  • the second split retainer 42 is inserted between the outer ring 11 and the inner ring 21 from one side of the shoulder 23a where the height of the inner ring 21 is low, and the ball 31 is inserted into the notch 50 formed in the second split retainer 42. It inserts so that it may fit, and the axial direction other side part of the 2nd division
  • the engagement claws formed in the respective divided holders 41 and 42 by fitting the second divided holder 42 into the first divided holder 41 as shown in FIGS. 46 and 51 are engaged with engaging recesses 47 and 52 provided in the other split cage, and the assembly of the deep groove ball bearing is completed.
  • the first divided holder 41 and the second divided hold are internally provided from both sides between the outer ring 11 and the inner ring 21.
  • the deep groove ball bearing A can be assembled by a simple operation of inserting the container 42 and fitting the second divided holder 42 into the first divided holder 41.
  • the deep groove ball bearing A When the above-described deep groove ball bearing A is used to support the cylindrical portions 8a and 8b formed at both ends of the differential case 3 shown in FIG. 12, the deep groove ball bearing A has a load driven shoulder 23b of the inner ring 21 with a final driven gear. Assembled on the 2nd side.
  • the ratio H 1 / d of the shoulder load H 1 on the thrust load side of the outer ring 11 to the ball diameter d of the ball 31 is in the range of 0.28 to 0.50, and the ball diameter of the ball Since the ratio H 2 / d of the shoulder height H 2 on the thrust load side of the inner ring 21 to d is in the range of 0.37 to 0.50, it is possible to reliably prevent the ball 31 from climbing.
  • a standard deep groove ball bearing 6208C having an inner ring outer diameter of ⁇ 53.1 mm and an outer ring inner diameter of ⁇ 68.1 mm is used as a comparative product, and the thrust load side of the inner ring is based on the standard deep groove ball bearing.
  • the deep groove ball bearing of the present invention showed a value higher by 305% than the comparative deep groove ball bearing.
  • the outer diameter of the shoulder of the inner ring where the thrust load (axial load) is not applied is changed from the standard ⁇ 53.1 mm to ⁇ 51.9 mm, and the inner diameter of the shoulder of the outer ring where the axial load is not applied is changed to the standard Even when the diameter was changed from ⁇ 68.1 mm to ⁇ 70.4 mm, even when the basic statically constant load Co was applied to the bearing, no shoulder climbing occurred.
  • the thrust force applied to the differential case 3 is the shoulder on the thrust load side of the inner ring 21 of the deep groove ball bearing A that receives the right end of the differential case 3 in FIG. 23b and a thrust load side shoulder 13a of the outer ring 11. Also in this case, it is possible to reliably prevent the ball 31 from climbing.
  • the outer ring 11 and the inner ring 21 are made of high carbon bearing steel with a large amount of carbon, the high carbon bearing steel is carbonitrided, quenched from a high temperature, and then tempered at a relatively low temperature. Since the amount of retained austenite in the surface layer is 15 to 20%, the fatigue strength of the raceway surface on which the balls 31 of the outer / inner rings 11 and 21 roll and move is extremely high, and the raceway surface is damaged. There is no.
  • the flow of lubricating oil that is rotated by contact with the first split cage 41 is the first. It becomes faster than the flow of the lubricating oil driven by the contact with the two-divided cage 42, the lubricating oil on the slow flow side is attracted to the fast flow side, and a pump action is generated inside the bearing. Due to the pump action, the lubricating oil flows in the direction indicated by the arrow in FIG. 1 and the inside of the bearing is forcibly lubricated, so that the lubricity of the deep groove ball bearing A can be improved.
  • a pair of opposed pocket claws 44 and 49 that embed the ball 31 in the open ends of the cutout portion 45 of the first divided holder 41 and the cutout portion 50 of the second divided holder 42.
  • a pair of opposed pocket claws 44 formed in the first divided holder 41 and a pair of opposed pocket claws 49 provided in the second divided holder 42 are oriented in opposite directions, and in the combined state Since the engagement claws 46 and 51 are engaged with the engagement recesses 47 and 52 and the first divided holder 41 and the second divided holder 42 are not separated in the axial direction, a large moment load is applied. Even if the ball 31 is delayed or advanced, the retainer 40 does not fall off.
  • the clearance ⁇ 1 of the circumferential clearance 60 formed between the engaging claws 46, 51 and the engaging recesses 47, 52 is set between the ball 31 and the notches 45, 50.
  • a large moment load is applied and the ball 31 is delayed and advanced, and the first split retainer 41 and the second split retainer 42, the engaging claws 46 and 51 do not come into contact with the opposite side surfaces of the engaging recesses 47 and 52 in the circumferential direction, which is effective in preventing damage to the engaging claws 46 and 51.
  • the clearance ⁇ 3 of the axial clearance 62 formed between the engaging claws 46, 51 and the engaging recesses 47, 52 is set between the ball 31 and the notches 45, 50.
  • the axial force in the direction away from the first divided cage 41 and the second divided cage 42 is applied to the first divided cage 41 and the second divided cage 42 by making the gap amount ⁇ 4 of the formed axial pocket gap 63 larger than the gap amount ⁇ 4.
  • the inner surfaces of the pair of pocket claws 44 and 49 abut against the outer peripheral surface of the ball 31, and the engagement claws 46 and 51 do not abut against the axial end surfaces of the engagement recesses 47 and 52. The effect of preventing the damage of 46 and 51 can be obtained.
  • the planar shape of the annular bodies 43 and 48 is larger than a half circle, and the cross-sectional shape is an arc shape.
  • the notches 45 and 50 are not limited to this.
  • a flat U-shape that forms a cylindrical pocket in the fitted state of the first divided holder 41 and the second divided holder 42 may be used.
  • the clearance ⁇ 5 of the circumferential clearance 64 formed between the engaging claws 46 and 51 and the engaging recesses 47 and 52 as shown in FIGS. Is larger than the clearance amount ⁇ 6 of the circumferential pocket clearance 66 formed between the ball 31 and the notches 45 and 50, a large moment load is applied and the ball 31 is delayed and advanced. Even if the split holder 41 and the second split holder 42 are relatively rotated, the engaging claws 46 and 51 do not come into contact with the side surfaces of the engaging recesses 47 and 52 that are opposed to each other in the circumferential direction. An effect can be obtained in preventing damage to the claws 46 and 51.
  • the weight ratio of the outer ring 11 and the inner ring 21 is 0.8 to 1.2% for carbon, 0.4 to 1.0% for silicon, 0.2 to 1.2% for chromium, and 0.
  • the outer austenite 11 and the inner ring are made to remain in the surface layer by setting the austenite amount in the surface layer to 25 to 50% and the austenite amount in the core portion to 15 to 20%.
  • the forming material and heat treatment of 21 are not limited to this.
  • the weight ratio of the outer ring 11 and the inner ring 21 is 0.6 to 1.2% carbon, 0.15 to 1.1% silicon, 2.0% or less chromium, and 0.3 to 1.5% manganese.
  • the carbon content exceeds 1.2% by weight, the material hardness is high even if spheroidizing annealing is performed, so that the cold workability is hindered, and the amount of cold work sufficient when performing cold work, The accuracy cannot be obtained. In addition, the carbonitriding process tends to become an excessively carburized structure, and there is a risk that the cracking strength is reduced.
  • the carbon content is less than 0.6% by weight, it takes a long time to secure the required surface hardness and the amount of retained austenite, or the necessary internal hardness is obtained by quenching after reheating. It becomes difficult to be.
  • Si content is 0.15 to 1.1% by weight. It is. If the silicon content is less than 0.15% by weight, the rolling fatigue life characteristics under lubrication with foreign matter will not be improved. On the other hand, if it exceeds 1.1% by weight, the hardness after normalization will be too high and cold working will occur. Inhibits sex.
  • Mn is effective in securing the quench hardening ability of the carbonitrided layer and the core. If the Mn content is less than 0.3% by weight, sufficient quenching and hardening ability cannot be obtained, and sufficient strength cannot be secured in the core. On the other hand, if the Mn content exceeds 1.5% by weight, the curing ability becomes excessively high, the hardness after normalization becomes high, and cold workability is hindered. In addition, the austenite is excessively stabilized and the amount of retained austenite in the core is excessively increased to promote a change in size over time.
  • the bearing steel may contain 2.0% by weight or less of chromium. By including 2.0% by weight or less of chromium, chromium carbide and nitride are precipitated in the surface layer portion, and the hardness of the surface layer portion is easily improved.
  • the Cr content is set to 2.0% by weight or less. If it exceeds 2.0% by weight, the cold workability is remarkably lowered, or even if the content exceeds 2.0% by weight, the hardness of the surface layer portion described above This is because the improvement effect is small.
  • the height H 3 of the shoulder 13 b on the thrust non-load side of the outer ring 11 and the height H 4 of the shoulder 23 a on the thrust non-load side of the inner ring 21 are the same as the shoulder of the standard deep groove ball bearing. However, it may be lower than the shoulder height of the standard deep groove ball bearing.
  • the ratio H 3 / d of the shoulder height H 3 to the sphere diameter d is set in the range of 0.08 to 0.25.
  • the ratio H 4 / d of the shoulder height H 4 to the ball diameter d of the ball 31 is in the range of 0.08 to 0.25.
  • the ratio r 1 / d / 2 of the radius of curvature r 1 of the outer ring raceway groove 12 to the radius d / 2 of the ball 31 is set in the range of 1.03 to 1.08, and the inner ring with respect to the radius d / 2 of the ball 31 is set.
  • the ratio r 2 / d / 2 of the radius of curvature r 2 of the raceway groove 22 should be in the range of 1.015 to 1.04 to prevent brittle peeling and suppress the decrease in the calculated load value.
  • FIG. 10 and 11 show another example of the cage 40.
  • FIG. The holder 40 shown in FIG. 10 includes split holders 71 and 72 that are divided into two in the axial direction.
  • Each of the split holders 71 and 72 includes a plurality of hemispherical pocket portions 73 and pocket portions 73.
  • a plurality of coupling plate parts 74 having the same width dimension as the width dimension are alternately and continuously corrugated in the circumferential direction, and the outer diameters of the coupling plate parts 74 of the two waveform division holders 71 and 72 are the same.
  • the position of the pocket portion 73 of one waveform division holder 71 is shifted to the inner diameter side with respect to the coupling plate portion 74, and the pocket portion 73 of the other waveform division holder 72 is outer diameter with respect to the coupling plate portion 74.
  • the one waveform segmented retainer 71 is inserted into the bearing from the side of the shoulder 13a having the higher height of the outer ring 11, and the other waveform segmented retainer 72 is lowered in the height of the outer ring 11.
  • Insert into the bearing from the shoulder 13b side, The pocket 75 is provided between the parts 73, and the two coupling plates 74 which abut each other so as to bind with rivets 76.
  • the cage 40 may be made of a metal plate press-molded product, or may be made of a synthetic resin molded product.
  • the waveform division holder 71 is inserted so that the ball 31 fits into the pocket portion 73 formed in the waveform division holder 71.
  • the other waveform division holder 72 is provided between the outer ring 11 and the inner ring 21 from one side of the shoulder 13 b on the thrust non-load side of the outer ring 11, and the ball 31 is inserted into a pocket portion 73 formed in the waveform division holder 72. Is inserted so that the coupling plate portion 74 of one waveform division holder 71 and the coupling plate portion 74 of the other waveform division holder 72 are brought into contact with each other, and the two coupling plate portions 74 are rivets. It joins by crimping 76.
  • the pocket portion 73 of one of the wave split cages 71 faces the shoulder 13a on the thrust load side of the outer ring 11 in the radial direction, and the pocket portion 73 is the coupling plate portion 74. Therefore, a gap is formed between the outer ring 11 and the shoulder 13a on the thrust load side.
  • the pocket portion 73 of the other waveform division holder 72 is opposed to the thrust load side shoulder 23b of the inner ring 21 in the radial direction, and the pocket portion 73 is displaced radially outward with respect to the coupling plate portion 74.
  • a gap is formed between the inner ring 21 and the shoulder 23b on the thrust load side.
  • the pocket portion 73 of the cage 40 does not interfere with the thrust load side shoulders 13a and 23b, and the outer ring 11 and the inner ring 21 can be smoothly rotated relative to each other. .
  • a ball non-contact portion 77 made of a concave portion is provided on the inner peripheral surface of the pocket 75 of each of the pocket portions 73 of the waveform division holders 71 and 72 shown in FIG.
  • the contact area with the ball 31 is 15% to 30% lower than the contact area with the ball 31 when the ball non-contact portion 77 is not provided.
  • the ball non-contact portion 77 formed of a recess on the inner peripheral surface of the pocket 75 of the pocket portion 73, the resistance when the lubricant passes through the pocket 75 and the amount of oil film to be sheared are reduced. Can be achieved, and a great effect can be obtained in reducing torque loss.

Landscapes

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

Abstract

L'invention concerne un roulement à billes à gorge profonde permettant d'empêcher complètement les billes de monter sur un épaulement, et présentant une longue durée de vie y compris en termes d'endurance au roulement. Des billes (31) sont insérées entre une rainure de chemin de roulement (12) de bague externe (11) et une rainure de chemin de roulement (22) de bague interne (21), et sont maintenues au moyen d'une cage (40). Parmi un ensemble de quatre épaulements formés individuellement des deux côtés de la rainure de chemin de roulement (12) de bague externe et de la rainure de chemin de roulement (22) de bague interne, la hauteur des épaulements d'une première paire (13a, 23b) diagonalement opposés, est plus importante que celles des épaulement de la paire restante (13b, 23a). Lorsque la hauteur du grand épaulement (13a) situé sur la bague externe (11) est représentée par (H1), que la hauteur du grand épaulement (23b) situé sur la bague interne (21) est représentée par (H2), et que le diamètre sphérique des billes (31) est représenté par (d), le rapport H1/d de la hauteur d'épaulement (H1) de la bague externe (11) par rapport au diamètre sphérique (d) des billes (31) est compris entre 0,28 et 0,50, et le rapport H2/d de la hauteur d'épaulement (H2) de la bague interne (21) par rapport au diamètre sphérique (d) des billes (31) est compris entre 0,37 et 0,50, ce qui empêche les billes (31) de monter sur les épaulements. En outre, l'endurance au roulement est améliorée par traitement thermique d'un acier à roulement constituant la matière des bagues externe (11) et interne (21).
PCT/JP2011/062959 2010-06-11 2011-06-06 Roulement à billes à gorge profonde WO2011155456A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-133915 2010-06-11
JP2010133915A JP5612912B2 (ja) 2010-06-11 2010-06-11 深みぞ玉軸受

Publications (1)

Publication Number Publication Date
WO2011155456A1 true WO2011155456A1 (fr) 2011-12-15

Family

ID=45098063

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/062959 WO2011155456A1 (fr) 2010-06-11 2011-06-06 Roulement à billes à gorge profonde

Country Status (2)

Country Link
JP (1) JP5612912B2 (fr)
WO (1) WO2011155456A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160238073A1 (en) * 2013-09-26 2016-08-18 Ntn Corporation Deep groove ball bearing
US20220025925A1 (en) * 2020-07-27 2022-01-27 Aktiebolaget Skf Deep groove ball bearing and differential
US20230047216A1 (en) * 2021-08-11 2023-02-16 Aktiebolaget Skf Deep groove ball bearing and applications thereof

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5751147B2 (ja) 2011-11-25 2015-07-22 株式会社デンソー モータ装置
JP6108779B2 (ja) * 2012-11-15 2017-04-05 Ntn株式会社 深みぞ玉軸受

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09264321A (ja) * 1996-03-29 1997-10-07 Ntn Corp アンギュラ玉軸受
JP2000145795A (ja) * 1998-11-06 2000-05-26 Ntn Corp 深みぞ玉軸受
JP2007155022A (ja) * 2005-12-06 2007-06-21 Nsk Ltd 転動装置
JP2010112461A (ja) * 2008-11-06 2010-05-20 Ntn Corp 転がり軸受用保持器及び転がり軸受

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08296650A (ja) * 1995-02-28 1996-11-12 Ntn Corp 玉軸受
JP3905429B2 (ja) * 2001-11-29 2007-04-18 Ｎｔｎ株式会社 軸受部品の熱処理方法および軸受部品
JP2004011712A (ja) * 2002-06-05 2004-01-15 Nsk Ltd 転がり軸受、これを用いたベルト式無段変速機
JP5233305B2 (ja) * 2008-02-12 2013-07-10 日本精工株式会社 ころ軸受及びその製造方法
JP2009270173A (ja) * 2008-05-09 2009-11-19 Nsk Ltd ラジアル軸受用軌道輪の熱処理方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09264321A (ja) * 1996-03-29 1997-10-07 Ntn Corp アンギュラ玉軸受
JP2000145795A (ja) * 1998-11-06 2000-05-26 Ntn Corp 深みぞ玉軸受
JP2007155022A (ja) * 2005-12-06 2007-06-21 Nsk Ltd 転動装置
JP2010112461A (ja) * 2008-11-06 2010-05-20 Ntn Corp 転がり軸受用保持器及び転がり軸受

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160238073A1 (en) * 2013-09-26 2016-08-18 Ntn Corporation Deep groove ball bearing
US20220025925A1 (en) * 2020-07-27 2022-01-27 Aktiebolaget Skf Deep groove ball bearing and differential
US11614121B2 (en) * 2020-07-27 2023-03-28 Aktiebolaget Skf Deep groove ball bearing and differential
US20230047216A1 (en) * 2021-08-11 2023-02-16 Aktiebolaget Skf Deep groove ball bearing and applications thereof
US11859661B2 (en) * 2021-08-11 2024-01-02 Aktiebolaget Skf Deep groove ball bearing and applications thereof

Also Published As

Publication number Publication date
JP2011256977A (ja) 2011-12-22
JP5612912B2 (ja) 2014-10-22

Similar Documents

Publication Publication Date Title
EP3372852B1 (fr) Dispositif de support de rotation pour arbre-pignon
US8322931B2 (en) Rotation support apparatus
WO2013085033A1 (fr) Composants de palier, palier à roulement, et procédés de fabrication de ces derniers
JP5982782B2 (ja) 風力発電設備用転がり軸受
US10890213B2 (en) Tapered roller bearing
WO2003081062A1 (fr) Roulement a billes pour transmission de type non etagee a courroie
JP5612912B2 (ja) 深みぞ玉軸受
US8794843B2 (en) Rotation support device for pinion shaft
JP2011220357A (ja) 遊星歯車装置
JP5168898B2 (ja) 転動軸
JP2005214390A (ja) ニードル軸受、遊星歯車機構及びピニオンシャフト
US7841773B2 (en) Tapered roller bearing
EP4001680B1 (fr) Roulement à rouleaux coniques
JP7394939B2 (ja) 円すいころ軸受
JP2006112558A (ja) 円すいころ軸受
JP2005140275A (ja) プラネタリギヤ装置
JP2008150687A (ja) 車輪支持用転がり軸受装置
JP2007051714A (ja) 円錐ころ軸受、及びこれを用いた車両用ピニオン軸支持装置
JP2003343577A (ja) 転がり軸受、これを用いたベルト式無段変速機
JP2006342904A (ja) ピニオンシャフト及びプラネタリギヤ装置
JP4269583B2 (ja) 転がり軸受、これを用いたベルト式無段変速機
JP2005344783A (ja) スラスト針状ころ軸受
JP2001003139A (ja) 円錐ころ軸受および車両用歯車軸支持装置
JP2009174691A (ja) トランスミッション用玉軸受
JP2003184870A (ja) ころ軸受

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11792413

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11792413

Country of ref document: EP

Kind code of ref document: A1