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WO2025053031A1 - Roulement à billes à contact oblique et mécanisme de rotation - Google Patents

Roulement à billes à contact oblique et mécanisme de rotation Download PDF

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Publication number
WO2025053031A1
WO2025053031A1 PCT/JP2024/030844 JP2024030844W WO2025053031A1 WO 2025053031 A1 WO2025053031 A1 WO 2025053031A1 JP 2024030844 W JP2024030844 W JP 2024030844W WO 2025053031 A1 WO2025053031 A1 WO 2025053031A1
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WO
WIPO (PCT)
Prior art keywords
ball bearing
inner ring
angular contact
balls
angular
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/JP2024/030844
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English (en)
Japanese (ja)
Inventor
康由 林
広道 國米
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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
Priority claimed from JP2023145527A external-priority patent/JP2025038740A/ja
Priority claimed from JP2023145621A external-priority patent/JP2025038796A/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2025053031A1 publication Critical patent/WO2025053031A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • 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
    • F16C33/32—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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/031—Gearboxes; Mounting gearing therein characterised by covers or lids for gearboxes

Definitions

  • the present invention relates to angular ball bearings and rotation mechanisms used, for example, in the main bearing parts of reducers in robots or construction machinery, and is a technology specialized for compactness, high load capacity, and high rigidity.
  • Patent Document 1 The following prior art rolling bearing without a cage (full ball type) is known (Patent Document 1).
  • This rolling bearing has only a large number of rolling elements arranged between an inner ring and an outer ring, the rolling elements being made of martensitic stainless steel, and the surfaces of the rolling elements have a nitrided layer with a hardness of Hv 1200 to 1500.
  • bearings used in the main bearing parts of reducers in robots or construction machinery generally require a long life, high moment rigidity, and compactness. This means that there is a demand for improving the rated load within a certain bearing size, which necessitates an increase in the ball size or the number of balls. Increasing the ball size poses the problem of reduced bearing rigidity because the raceways become thinner.
  • there is a method of using full ball bearings without a cage in order to increase the number of balls In order to increase the number of balls.
  • the relative sliding speeds between adjacent balls in contact are in opposite directions, which causes "reverse sliding" in the contact area between the balls, making it a challenge to find ways to suppress ball wear.
  • the above-mentioned conventional technology solves this problem by providing a nitride layer on the surface of the ball, making the surface very hard, at HV1200 to 1500, and thus suppressing ball wear.
  • the problem with nitrided balls with this surface hardness is that the heat treatment costs are high.
  • the object of the present invention is to provide an angular contact ball bearing and a rotation mechanism that can suppress ball wear even if reverse sliding occurs between the balls, and can also reduce costs.
  • the angular contact ball bearing according to a first aspect of the present invention is an angular contact ball bearing without a cage, comprising an inner ring, an outer ring, and a plurality of balls interposed between the inner ring and the outer ring,
  • the surface roughness of the balls is 0.06 ⁇ m Ra or less
  • the kinetic viscosity of the lubricant (40° C.) is 46 cst or more and 220 cst or less.
  • the so-called full-ball angular contact ball bearing has a higher ball packing rate than an angular contact ball bearing with a cage, which results in a relatively higher load capacity and moment rigidity.
  • the balls come into contact with each other due to the relative difference in revolution speed, and the relative sliding speeds of adjacent contacting balls are in opposite directions, resulting in "reverse sliding" at the contact area between the balls.
  • the lubricant may be a grease, and the consistency of the grease may be from No. 1 to No. 00.
  • the above-mentioned consistency is a value indicated by the JIS (Japanese Industrial Standards) classification.
  • JIS Japanese Industrial Standards
  • the worked consistency of "1" is "310 to 340”
  • the worked consistency of "0" is "355 to 385".
  • the worked consistency of "00” is "400 to 430".
  • These JIS consistency numbers 1, 0, and 00 correspond to NLGI (National Lubricating Grease Institute) consistency numbers 1, 0, and 00, respectively. It was found that when the lubricant is grease, grease that flows easily between the balls has a greater effect in suppressing ball wear. The ease with which grease flows between the balls varies specifically with the consistency classification.
  • Greases with consistency classifications in the range of No. 1 to No. 00 have relatively good ability to flow between the balls, and can further enhance the effect of suppressing ball wear.
  • the ball may have a grade of 40 or less.
  • the above grades are values stipulated in JIS B1501 of the Japanese Industrial Standards. By setting the ball grade to 40 or less, it is possible to select balls with a surface roughness of 0.06 ⁇ m Ra or less.
  • the surface roughness of the balls may be 0.04 ⁇ m Ra or less, and the kinetic viscosity of the lubricant (40°C) may be 68 cst or more and 150 cst or less. In this case, the oil film between the balls is more effectively formed, and the effect of suppressing ball wear can be further improved.
  • the material of the balls may be bearing steel. In this case, manufacturing costs can be reduced compared to using balls made of, for example, martensitic stainless steel, ceramics, etc.
  • the material of the balls is bearing steel, they may be subjected to a surface hardening treatment.
  • a surface hardening treatment is nitriding.
  • JP 2005-201294 A Japanese Patent No. 4,515,039 A
  • the angular ball bearing of JP 2005-201294 A is a multi-point contact type in which balls contact the raceway surfaces of the inner and outer rings at two points each with a required contact angle.
  • the angular ball bearing in Patent No. 4,515,039 is a double-row integral angular ball bearing which has multiple rows of balls with different pitch circle diameters and a cage which holds the rows of balls, in which the balls in each row contact the inner and outer ring raceway surfaces at a predetermined contact angle.
  • a ball bearing has a contact ellipse, which is the contact point between the raceway and the ball where the load acts. When the ball rolls, it cannot roll purely at all points on this contact ellipse, and slippage (differential slippage) occurs within the contact ellipse. Multi-point contact angular ball bearings contact one ball at two contact angles, which creates the problem of large differential slip at one of the contact points, accelerating wear on the raceway surface.
  • Double-row integral angular contact ball bearings have a thin raceway shoulder because the balls are arranged in double rows. For this reason, when a moment load is applied to double-row integral angular contact ball bearings, the elastic deformation of the shoulder can reduce moment rigidity.
  • double-row integral angular contact ball bearings have a complex raceway shape, which makes it difficult and costly to manufacture the raceways.
  • An angular ball bearing according to a second aspect of the present invention is an angular ball bearing including an inner ring, an outer ring, and a plurality of balls interposed between the inner ring and the outer ring,
  • the contact angle is 40° or more and 50° or less
  • a ratio W/Dw of an axial length W of an outer peripheral surface on a back surface side of the inner ring to a ball diameter Dw which is a diameter of the ball is 0.15 or greater and 0.35 or less
  • a ratio V/Dw of an axial length V of an inner peripheral surface on a back surface side of the outer ring to a ball diameter Dw is 0.15 or more and 0.35 or less.
  • the ball filling rate can be improved compared to an angular contact ball bearing with a cage.
  • a rotation mechanism is a rotation mechanism including an angular contact ball bearing including an inner ring, an outer ring, and a plurality of balls interposed between the inner ring and the outer ring, An inner ring shoulder deformation suppression means is provided to suppress deformation of the inner ring shoulder,
  • the angular contact ball bearing is The contact angle is 40° or more and 50° or less,
  • a ratio V/Dw of an axial length V of an inner peripheral surface on a back surface side of the outer ring to a ball diameter Dw which is a diameter of the ball is 0.15 or more.
  • the "inner race shoulder" is the outer circumferential portion on the back side of the inner race.
  • the ball filling rate can be improved compared to an angular contact ball bearing with a cage, which contributes to higher rigidity and higher load capacity of the rotating mechanism.
  • the inner ring shoulder deformation suppression means may be a means for integrating the inner ring with the rotating shaft of the rotating mechanism. In this case, it is possible to make the inner ring shoulder thicker than the inner ring shoulder of a typical angular ball bearing. In that case, there will be no decrease in moment rigidity if the contact angle is in the range of 40° to 50° and V/Dw is in the range of 0.15 or more.
  • the inner ring shoulder deformation suppression means may be such that the shoulder diameter of the member facing the back surface of the inner ring is equal to or greater than the inner ring shoulder diameter. In this case as well, deformation of the inner ring shoulder can be suppressed, and a decrease in moment rigidity can be suppressed.
  • the member facing the back surface of the inner ring may be the rotating shaft of the rotating mechanism or an annular regulating member. If the shaft shoulder of the rotating shaft is made equal to or larger than the inner ring shoulder diameter, the number of parts can be reduced and the structure can be simplified compared to providing an annular regulating member. If the annular regulating member is made equal to or larger than the inner ring shoulder diameter, the diameter dimension of the rotating shaft can be shortened.
  • a rotation mechanism is a rotation mechanism including an angular contact ball bearing including an inner ring, an outer ring, and a plurality of balls interposed between the inner ring and the outer ring, the outer ring is integrally provided with a housing of the rotation mechanism,
  • the angular contact ball bearing is The contact angle is 40° or more and 50° or less,
  • the ratio W/Dw of the axial length W of the outer peripheral surface on the back surface side of the inner ring to the ball diameter Dw which is the diameter of the ball is 0.15 or more.
  • the ball filling rate can be improved compared to an angular contact ball bearing with a cage, which contributes to higher rigidity and higher load capacity of the rotating mechanism.
  • the reducer of the present invention is equipped with any of the above-described rotation mechanisms of the present invention. Therefore, the effects described above for the rotation mechanism of the present invention can be obtained.
  • FIG. 1 is a vertical sectional view of an angular contact ball bearing according to a first embodiment of the present invention
  • FIG. 2 is a perspective view of the angular contact ball bearing.
  • 4 is a conceptual diagram illustrating reverse sliding between balls in the angular contact ball bearing.
  • FIG. FIG. 4 is a vertical cross-sectional view showing an example of a back-to-back assembly of the angular ball bearings.
  • FIG. 6 is a longitudinal sectional view of a rotation mechanism including an angular ball bearing according to a second embodiment of the present invention.
  • FIG. 11 is a longitudinal sectional view of a rotation mechanism including an angular ball bearing according to a third embodiment of the present invention.
  • FIG. 11 is a longitudinal sectional view of an angular ball bearing according to a fourth embodiment of the present invention.
  • 4 is a conceptual diagram illustrating the relationship between the contact angle and moment stiffness of the angular ball bearing.
  • FIG. FIG. 4 is a vertical cross-sectional view showing an example of a back-to-back assembly of the angular ball bearings.
  • FIG. 13 is an enlarged cross-sectional view of a main portion of a rotation mechanism including an angular ball bearing according to a fifth embodiment of the present invention.
  • FIG. 13 is an enlarged cross-sectional view of a main portion of a rotation mechanism including an angular ball bearing according to a sixth embodiment of the present invention.
  • FIG. 13 is an enlarged cross-sectional view of a main portion of a rotation mechanism including an angular ball bearing according to a seventh embodiment of the present invention.
  • FIG. 13 is an enlarged cross-sectional view of a main portion of a rotation mechanism including an angular ball bearing according to an eighth embodiment of the present invention.
  • FIG. 2 is a vertical cross-sectional view showing the entire rotation mechanism of each embodiment of the present invention.
  • FIG. 1 An angular contact ball bearing according to an embodiment of the present invention will be described with reference to Figures 1 to 3.
  • This angular contact ball bearing is used, for example, as a main bearing portion of a reducer in a robot, construction machine, or the like.
  • the angular ball bearing may be simply referred to as the "bearing”.
  • the angular contact ball bearing 1 is a so-called full-ball angular contact ball bearing without a cage, which includes an inner ring 2, an outer ring 3, and a number of balls 4 interposed between raceway surfaces 2a, 3a of the inner and outer rings 2, 3.
  • the inner and outer rings 2, 3 and the balls 4 are made of high carbon chromium bearing steel such as SUJ2.
  • the term "axial direction” refers to a direction along the bearing center line of the angular ball bearing 1.
  • radial direction refers to a direction perpendicular to the straight line that constitutes the "axial direction.”
  • the raceway surface 3a is connected to the front surface of the outer ring 3 via a counterbore 3b.
  • the inner peripheral surface 3d on the back surface side of the outer ring 3 is located radially inward from the counterbore 3b of the outer ring 3.
  • the raceway surface 2a is connected to the front surface of the inner ring 2 via a counterbore 2b.
  • the outer peripheral surface 2d on the back surface side of the inner ring 2 is formed between the raceway surface 2a of the inner ring 2 and the back surface 2c of the inner ring 2.
  • the outer peripheral surface 2d of the inner ring 2 is located radially outward from the counterbore 2b of the inner ring 2.
  • the front surfaces of the inner and outer rings 2 and 3 refer to the side surfaces that do not support axial loads
  • the back surfaces 2c and 3c of the inner and outer rings 2 and 3 refer to the side surfaces that support axial loads.
  • the angular ball bearing 1 does not have a cage (all balls) in order to increase the number of balls, and the improved ball packing rate improves the load capacity and moment rigidity compared to an angular ball bearing with a cage.
  • the consistency is a value determined by the test method of JIS K2220, and in the present embodiment, it is expressed by the JIS classification.
  • the kinetic viscosity is a value at 40° C. determined by the test method of JIS K2283.
  • the surface roughness of the balls is 0.04 ⁇ mRa or less and the kinetic viscosity of the lubricant (40° C.) is in the range of 68 cst to 150 cst as in Examples 2 to 4, an oil film is formed even better between the balls and the effect of suppressing ball wear can be further improved.
  • This configuration which combines a lubricant with an optimum kinetic viscosity with an optimum ball surface roughness, can reduce costs compared to the conventional technique of providing a nitride layer on the ball surface.
  • the kinetic viscosity (40°C) of the lubricant is 320 cst, regardless of the surface roughness of the balls, heat generation increases and an oil film is difficult to form, resulting in a low wear suppression effect.
  • balls of grade 24 or less When the surface roughness of the ball is 0.04 ⁇ m Ra or less, balls of grade 24 or less may be selected, and when the surface roughness of the ball is 0.06 ⁇ m Ra or less, balls of grade 40 or less may be selected.
  • the lubricant is grease
  • those that allow the grease to easily flow between the balls have a greater effect in suppressing ball wear.
  • the ease with which grease can flow between the balls varies specifically with the consistency classification. The higher the consistency (softer), the better the ability of grease to flow between the balls, and the lower the consistency (harder), the worse the ability of grease to flow.
  • Greases with consistency classifications in the range of No. 1 to No. 00 have relatively good ability to flow between the balls, and can further enhance the effect of suppressing ball wear. With a consistency classification lower than No. 2, the grease is hard and the grease does not flow well, which may result in a lower effect in suppressing wear.
  • the angular ball bearings 1 can be arranged in a back-to-back configuration as shown in FIG. 4 to increase the distance between the bearing load points, so that the allowable radial load and allowable moment load can be increased even if the angular ball bearings 1 are made smaller, i.e., more compact. Furthermore, by arranging the angular ball bearings 1 in a back-to-back configuration, they can withstand axial loads in both directions, and in addition, the rigidity of the bearing portion can be increased by applying preload. In the example shown in FIG.
  • an inner ring spacer 7 and an outer ring spacer 8 are interposed between the angular ball bearings 1, 1 adjacent to each other in the axial direction, but it is also possible to omit these spacers 7, 8 and arrange the angular ball bearings 1, 1 in a back-to-back configuration.
  • a rotation mechanism 9 may be provided with an angular ball bearing 1 in which the inner ring 2 and the shaft are integrated.
  • integrated means that the inner ring 2 and the shaft are not formed by combining a plurality of elements but are formed as a part or the whole of a single object from a single material by, for example, forging or machining.
  • This rotation mechanism 9 is a vehicle power unit, a so-called axle unit, provided on a vehicle, and includes a double-row angular ball bearing 1 assembled back-to-back, and a drive motor M with a power generating function.
  • the outer ring 3 of the angular ball bearing 1 is a rotating ring
  • the inner ring 2 integrated with the shaft is a fixed ring.
  • a brake rotor BR and a wheel are attached to a wheel mounting flange 3F provided on the outboard end of the outer ring 3 in a state where they overlap in the axial direction.
  • the rotation mechanism 9 in which the inner ring 2 and the shaft are integrated, it is possible to achieve high rigidity and high load capacity without increasing the size.
  • a rotation mechanism 9A may be provided with an angular ball bearing 1 in which the outer ring 3 and the housing 14 are integrated. Even in the case of the rotation mechanism 9A in which the outer ring 3 and the housing 14 are integrated, it is possible to achieve high rigidity and high load capacity without increasing the size.
  • At least one of the inner and outer rings and the balls may be made of a material other than bearing steel, such as martensitic stainless steel or ceramics. It is also possible to use angular contact ball bearings in face-to-face or parallel combinations. It is also possible to use angular contact ball bearings in a multi-row combination of three or more rows. The angular ball bearing and the rotation mechanism can also be used for purposes other than the reducer.
  • the material of the balls is bearing steel, they may be subjected to a surface hardening treatment.
  • a surface hardening treatment is nitriding.
  • the angular ball bearing 1 according to the fourth embodiment has the same schematic configuration as the angular ball bearing according to the first embodiment described above.
  • the same components as those in the first embodiment are given the same reference numerals, and detailed description thereof will be omitted.
  • the angular ball bearing 1 according to the embodiment of the present invention is cage-less (total balls) in order to increase the number of balls, and the improved packing rate of the balls 4 improves the load capacity and moment rigidity compared to an angular ball bearing with a cage.
  • the bearing size is an angular contact ball bearing with a ball diameter/PCD ratio of 0.05 to 0.10.
  • 20 types of angular contact ball bearings (Comparative Examples 1 to 16, Examples 1 to 4) were assumed, with a contact angle ⁇ in the range of 20° to 55°, a ratio W/Dw of the axial length W of the outer peripheral surface 2d on the back side of the inner ring 2 to the ball diameter Dw (diameter of the balls 4) in the range of 0.07 to 0.4, and a ratio V/Dw of the axial length V of the inner peripheral surface 3d on the back side of the outer ring 3 to the ball diameter Dw (diameter of the balls 4) in the range of 0.07 to 0.4.
  • Table 2 shows the load capacity, moment stiffness (when the raceway is rigid), and deformation of the shoulders 5 and 6 for the comparative examples and examples in which the respective parameters were changed.
  • ⁇ indicates that the load capacity is feasible and can be implemented efficiently
  • ⁇ indicates that the performance is inferior to ⁇ but it is feasible
  • ⁇ indicates that the performance is inferior to ⁇ and it is not recommended to implement
  • ⁇ indicates that it is not feasible.
  • the V/Dw arrow indicates that the value is the same as the W/Dw value in the same column.
  • Moment stiffness represents the stiffness of an angular contact ball bearing, and is expressed as the load moment value required to tilt a unit angle (1 arcmin.).
  • the moment stiffness in this example represents the case where the raceway is considered to be a rigid body, and the ⁇ , ⁇ , ⁇ and ⁇ symbols in Table 2 for moment stiffness have the same definition as the load capacity.
  • the shoulder deformation is indicated by an ⁇ if there is almost no shoulder deformation and no decrease in moment rigidity, and an X if the shoulder deformation decreases moment rigidity. From Table 2, it can be seen that Examples 1, 2, 3, and 4 are capable of achieving load capacity and moment rigidity or can achieve them efficiently, and do not experience a decrease in moment rigidity due to deformation of the shoulder portion.
  • an inner ring spacer 7 and an outer ring spacer 8 are interposed between the angular ball bearings 1, 1 adjacent to each other in the axial direction, but it is also possible to omit these spacers 7, 8 and arrange the angular ball bearings 1, 1 in a back-to-back configuration.
  • FIG. 10 is an enlarged cross-sectional view of a main portion of a rotation mechanism 9 including an angular ball bearing according to a fifth embodiment.
  • the rotating mechanism 9 may be provided with an inner ring shoulder deformation suppression means 11 for suppressing deformation of the inner ring shoulder 5.
  • the inner ring shoulder deformation suppression means 11 is formed by integrating the inner ring 2 of the angular ball bearing 1 on the left side of Figure 10 with the rotating shaft 12 of this rotating mechanism 9.
  • integrated means that the inner ring 2 and the rotating shaft 12 are not formed by combining multiple elements, but are formed as part or the whole of a single object from a single material by, for example, forging, machining, etc.
  • the inner ring shoulder deformation suppression means may set the shoulder diameter D1 of the member facing the back surface 2c of the inner ring 2 to be equal to or larger than the inner ring shoulder diameter D2.
  • the member facing the back surface 2c of the inner ring 2 is the rotating shaft 12 of the rotation mechanism 9.
  • the member facing the back surface of the inner ring 2 may be an annular regulating member 13.
  • the regulating member 13 is formed, for example, in a rectangular cross section, and is interposed between the inner surface of the flange portion 12a of the rotating shaft 12 and the back surface 2c of the inner ring 2.
  • the outer diameter, i.e., shoulder diameter D3 of the regulating member 13 is set to be equal to or larger than the inner ring shoulder diameter D2, thereby making it possible to reduce the diameter dimension of the rotating shaft 12.
  • the same effects as those of the rotation mechanism of the fifth embodiment are achieved.
  • outer ring and housing integrated 13 in a rotation mechanism 9 equipped with a full-ball angular contact ball bearing 1, the outer ring 3 may be provided integrally with a housing 14 of the rotation mechanism 9.
  • integral means that the outer ring 3 and the housing 14 are not formed by combining a plurality of elements but are formed as a part or the whole of a single object from a single material by, for example, forging, machining, etc.
  • the rotation mechanism 9 shown in Fig. 14 is a vehicle power unit, a so-called axle unit, provided on a vehicle, and includes a double-row angular ball bearing 1 assembled back-to-back, and a drive motor M with a power generating function.
  • the outer ring 3 of the angular ball bearing 1 is a rotating ring
  • the inner ring 2 integrated with the shaft is a fixed ring.
  • a brake rotor BR and a wheel are attached to a wheel mounting flange 3F provided on the outboard end of the outer ring 3 in a state where they overlap in the axial direction.
  • the reducer 10 to 13 may be used, for example, in the main bearing portion of a reducer 10 of a robot, a construction machine, etc.
  • the reducer 10 may include any of the rotation mechanisms 9 described above. It is also possible to use angular contact ball bearings in face-to-face or parallel combinations. It is also possible to use angular contact ball bearings in a multi-row combination of three or more rows. The angular ball bearing and the rotation mechanism can also be used for purposes other than the reducer.

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

Abstract

L'invention concerne un roulement à billes à contact oblique et un mécanisme de rotation avec lesquels l'usure des billes peut être atténuée même lorsque les billes glissent les unes contre les autres, et le coût peut être réduit. Un roulement à billes à contact oblique (1) est un roulement à billes à contact oblique dépourvu de dispositif de retenue et comprenant une bague interne (2), une bague externe (3) et une pluralité de billes (4) interposées entre la bague interne (2) et la bague externe (3). La rugosité de surface des billes (4) est inférieure ou égale à 0,06 µmRa, et la viscosité cinématique (40°C) d'un lubrifiant est de 46 à 220 cst. Lorsque le lubrifiant est de la graisse, la consistance de la graisse varie de N° 1 à N° 00. La rugosité de surface des billes (4) est, de préférence, inférieure ou égale à 0,04 µmRa, et la viscosité cinématique (40°C) du lubrifiant est, de préférence, de 68 à 150.
PCT/JP2024/030844 2023-09-07 2024-08-29 Roulement à billes à contact oblique et mécanisme de rotation Pending WO2025053031A1 (fr)

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JP2023145527A JP2025038740A (ja) 2023-09-07 2023-09-07 アンギュラ玉軸受および回転機構
JP2023-145621 2023-09-07
JP2023-145527 2023-09-07
JP2023145621A JP2025038796A (ja) 2023-09-07 2023-09-07 アンギュラ玉軸受および回転機構

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004092686A (ja) * 2002-08-29 2004-03-25 Nsk Ltd 転がり軸受
JP2006220174A (ja) * 2005-02-08 2006-08-24 Nsk Ltd 複列玉軸受
JP2011038591A (ja) * 2009-08-11 2011-02-24 Nsk Ltd 転動装置
JP2012229783A (ja) * 2011-04-27 2012-11-22 Nsk Ltd アンギュラ玉軸受
JP2019044061A (ja) * 2017-08-31 2019-03-22 株式会社服部商店 グリース組成物およびその製造方法、並びに転動装置
JP2022073906A (ja) * 2020-10-30 2022-05-17 Ntn株式会社 転動部材及び転がり軸受

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004092686A (ja) * 2002-08-29 2004-03-25 Nsk Ltd 転がり軸受
JP2006220174A (ja) * 2005-02-08 2006-08-24 Nsk Ltd 複列玉軸受
JP2011038591A (ja) * 2009-08-11 2011-02-24 Nsk Ltd 転動装置
JP2012229783A (ja) * 2011-04-27 2012-11-22 Nsk Ltd アンギュラ玉軸受
JP2019044061A (ja) * 2017-08-31 2019-03-22 株式会社服部商店 グリース組成物およびその製造方法、並びに転動装置
JP2022073906A (ja) * 2020-10-30 2022-05-17 Ntn株式会社 転動部材及び転がり軸受

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