WO2023127384A1 - 保持器及び軸受装置 - Google Patents

保持器及び軸受装置 Download PDF

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Publication number
WO2023127384A1
WO2023127384A1 PCT/JP2022/044221 JP2022044221W WO2023127384A1 WO 2023127384 A1 WO2023127384 A1 WO 2023127384A1 JP 2022044221 W JP2022044221 W JP 2022044221W WO 2023127384 A1 WO2023127384 A1 WO 2023127384A1
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WO
WIPO (PCT)
Prior art keywords
retainer
holding portion
connecting portion
wall
bearing device
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.)
Ceased
Application number
PCT/JP2022/044221
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
慎一郎 林
裕成 迫田
康宏 荒木
雅之 佐藤
聡 島崎
大樹 高橋
雄介 萬
慎吾 今井
文 菊池
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.)
NSK Ltd
Original Assignee
NSK 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
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to EP22915615.3A priority Critical patent/EP4459144A4/en
Priority to US18/723,014 priority patent/US20250146529A1/en
Priority to CN202280084108.6A priority patent/CN118575007A/zh
Priority to JP2023570746A priority patent/JPWO2023127384A1/ja
Publication of WO2023127384A1 publication Critical patent/WO2023127384A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16C19/04—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
    • 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
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • 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
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • 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
    • F16C33/41—Ball cages comb-shaped
    • F16C33/418—Details of individual pockets, e.g. shape or ball retaining means

Definitions

  • the present disclosure relates to retainers and bearing devices.
  • the bearing device has a retainer to keep the distance between the balls constant.
  • An example of a retainer is a crown-type retainer.
  • the crown-type retainer disclosed in Patent Document 1 below has a plurality of column portions provided at equal intervals in the circumferential direction around the axial center of the inner ring, and a plurality of column connecting portions connecting the column portions. there is Spaces between the pillars are called pockets, and a ball is placed in each pocket. Further, in the retainer disclosed in Patent Document 1 below, the column connecting portion is thicker than the column portion. As a result, even if a circumferential load is applied to the column, the retainer is less likely to be damaged.
  • the crown-shaped retainer of Patent Document 2 below has a plurality of retaining portions provided at equal intervals in the circumferential direction, and retaining portion connecting portions arranged between the retaining portions.
  • the holding portion has a U shape (C shape) when viewed from the radial direction. That is, the holding portion has a bottom wall extending in the circumferential direction and a pair of opposed walls extending in the axial direction from both circumferential ends of the bottom wall. A space between a pair of opposing walls is called a pocket, in which balls are placed.
  • the connecting portion of the holding portion disclosed in Patent Document 2 has the same thickness in the radial direction as that of the opposing wall, and has high rigidity.
  • the axial load, radial load, moment load, etc. are combined and input to the bearing device, causing the balls to slip.
  • the balls move in the circumferential direction around the axial center of the inner ring, but their speed slows down and then increases (hereinafter referred to as "advance or lag of the balls").
  • advance or lag of the balls When the speed of one ball changes and the ball contacts the post (or opposing wall) of the cage, the relative position between the cage and the ball changes, causing another ball to hit the other post (or facing wall) collide. Then, another ball pushed by another column (or opposing wall) slips on the raceway surface.
  • the torque from the inner ring to the outer ring fluctuates.
  • the present disclosure has been made in view of the above, and aims to provide a retainer and a bearing device capable of suppressing torque fluctuations.
  • a retainer is arranged between an inner ring and an outer ring of a bearing device, and provided at equal intervals in the circumferential direction around the axial center of the inner ring.
  • a plurality of pillars and a plurality of pillar connecting portions that connect the pillars are provided.
  • a pocket in which a ball is placed is formed between the plurality of pillars.
  • the column portion has an end face facing one of the axial directions parallel to the axis. The end face is provided with a recess recessed in the other axial direction.
  • the pillars are provided with recesses and have low rigidity. Therefore, when the speed of the ball changes and the ball contacts the column, the column deforms and absorbs the contact load of the ball. As described above, it is possible to suppress the change in the relative position between the retainer and the balls due to the contact of the balls, thereby suppressing the fluctuation of the torque.
  • the column portion is provided with an opening that opens the concave portion radially inward.
  • the pillar has a tip wall that serves as a bottom wall of the recess. The tip wall is offset from the center of the ball in the axial direction.
  • the column portion is provided with a through-hole penetrating in a radial direction.
  • the rigidity of the column portion is further lowered, and the load that can be absorbed is increased. Therefore, fluctuations in torque are reliably suppressed.
  • a retainer is arranged between an inner ring and an outer ring of a bearing device, and is provided at equal intervals in the circumferential direction around the axial center of the inner ring. and a plurality of holding portion connecting portions that connect the holding portions to each other.
  • the holding portion has a bottom wall extending in the circumferential direction, and a pair of opposing walls extending in the axial direction parallel to the axis from both circumferential ends of the bottom wall. A space between the pair of opposing walls forms a pocket in which a ball is placed.
  • the radial thickness of the holding portion connecting portion is smaller than the radial thickness of the opposing wall.
  • the radially central portion of the holding portion connecting portion is arranged radially inwardly or radially outwardly with respect to an imaginary circle passing through the center of each ball.
  • the connecting part of the holding part is radially displaced (offset) with respect to the virtual circle passing through the center of the ball.
  • the connecting portion of the holding portion is easily bent.
  • the connecting portion of the holding portion is thinner than the conventional one and is easily deformable (flexible).
  • the radial center portion of the holding portion connecting portion is arranged radially outward with respect to an imaginary circle passing through the center of each of the balls.
  • the holding part connecting part has a longer circumferential length and is more flexible when arranged radially outward than when arranged radially inward with respect to the imaginary circle. Therefore, the load absorbed by the deformation of the connecting portion of the holding portion is increased, and the fluctuation of the torque is reliably suppressed.
  • the retainer connecting portion is bent.
  • the connecting portion of the holding portion when a load is applied in the circumferential direction, the connecting portion of the holding portion has a shape that is more easily deformed. Therefore, the load absorbed by the deformation of the connecting portion of the holding portion is further increased, and the fluctuation of the torque is reliably suppressed.
  • a retainer is arranged between an inner ring and an outer ring of a bearing device, and is provided at equal intervals in the circumferential direction around the axial center of the inner ring. and a plurality of holding portion connecting portions that connect the holding portions to each other.
  • the holding portion has a bottom wall extending in the circumferential direction, and a pair of opposing walls extending in the axial direction parallel to the axis from both circumferential ends of the bottom wall. A space between the pair of opposing walls forms a pocket in which a ball is placed.
  • the holding portion connecting portion is bent.
  • the connecting portion of the holding portion when a load is applied in the circumferential direction, the connecting portion of the holding portion has a shape that is easily deformed. Therefore, the contact load with the ball input to the opposing wall is absorbed by the deformation of the connecting portion of the holding portion. As described above, it is possible to suppress the change in the relative position between the retainer and the balls due to the contact of the balls, thereby suppressing the fluctuation of the torque.
  • a bearing device includes an inner ring having an outer peripheral raceway surface provided on its outer peripheral surface, an outer ring having an inner peripheral raceway surface provided on its inner peripheral surface, and the outer peripheral raceway. It comprises a plurality of balls arranged between the surface and the inner circumferential raceway surface, and the retainer described above.
  • the bearing device of the present disclosure it is suppressed that the balls come into contact with each other and the relative position between the retainer and the balls changes, and torque fluctuations are suppressed.
  • FIG. 1 is a radial cross-sectional view of the bearing device of Embodiment 1.
  • FIG. 2 is a perspective view of the retainer of Embodiment 1.
  • FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2.
  • FIG. 4 is a radial cross-sectional view of the bearing device of Modification 1.
  • FIG. 5 is a perspective view of a retainer of Modification 1.
  • FIG. FIG. 6 is a radial cross-sectional view of the bearing device of Modification 2.
  • FIG. 7 is a perspective view of a retainer of Modification 2.
  • FIG. 8 is a perspective view of a retainer of Modification 3.
  • FIG. FIG. 1 is a radial cross-sectional view of the bearing device of Embodiment 1.
  • FIG. 2 is a perspective view of the retainer of Embodiment 1.
  • FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2.
  • FIG. FIG. 4 is
  • FIG. 9 is a side view of the bearing device of Embodiment 2 as seen from one axial direction.
  • 10 is a perspective view of the retainer of Embodiment 2.
  • FIG. 11 is an enlarged view enlarging a part of the bearing device of FIG. 9.
  • FIG. FIG. 12 is an enlarged view showing a case where a ball collides with an opposing wall in the bearing device of Embodiment 2.
  • FIG. 13 is an enlarged view of the bearing device of Modification 4 as seen from the axial direction.
  • FIG. 14 is an enlarged view of the bearing device of Modification 5 as seen from the axial direction.
  • 15 is a perspective view of the retainer of Embodiment 3.
  • FIG. 16 is a cross-sectional view taken along line XVI-XVI of FIG. 15.
  • FIG. 16 is a cross-sectional view taken along line XVI-XVI of FIG. 15.
  • FIG. 17 is an enlarged view showing a case where a ball collides with an opposing wall in the bearing device of Embodiment 3.
  • FIG. 18 is a perspective view of a retainer of Embodiment 4.
  • FIG. 19 is an enlarged view of the bearing device of Modification 6 viewed from the axial direction.
  • FIG. 1 is a radial cross-sectional view of the bearing device of Embodiment 1.
  • the bearing device 80 includes an annular inner ring 1, an annular outer ring 2 surrounding the outer circumference of the inner ring 1, a plurality of balls 3 arranged between the inner ring 1 and the outer ring 2, and a retainer. 4 and .
  • the direction parallel to the axis O of the inner ring 1 is called the axial direction.
  • One of the rotation directions about the axis O is called a first rotation direction L1
  • the opposite direction to the first rotation direction is called a second rotation direction L2 (see arrows in FIGS. 2 and 3).
  • the outer peripheral surface of the inner ring 1 is provided with an outer peripheral raceway surface 1a extending in the circumferential direction.
  • the inner peripheral surface of the outer ring 2 is provided with an inner peripheral raceway surface 2a extending in the circumferential direction.
  • the outer raceway surface 1a and the inner raceway surface 2a face each other in the radial direction.
  • groove shapes of the outer circumference raceway surface 1a and the inner circumference raceway surface 2a are not particularly limited. That is, the outer circumference raceway surface 1a and the inner circumference raceway surface 2a may have either circular arc shape or gothic arc shape.
  • the balls 3 are arranged between the outer circumference raceway surface 1a and the inner circumference raceway surface 2a.
  • An outer surface of the ball 3 (hereinafter referred to as a rolling contact surface 3a) is in contact with each of the outer circumference raceway surface 1a and the inner circumference raceway surface 2a.
  • the plurality of balls 3 are arranged around the axis O at regular intervals in the circumferential direction. As a result, the load acting from the inner ring 1 to the outer ring 2 (or the load acting from the outer ring 2 to the inner ring 1) is distributed evenly in the circumferential direction.
  • FIG. 2 is a perspective view of the retainer of Embodiment 1.
  • FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2.
  • FIG. The retainer 4 is an annular component made of resin. Note that the present disclosure is not limited to resin retainers. As shown in FIG. 2, the retainer 4 is arranged between a plurality of pillars 10 evenly arranged in the circumferential direction around the axis O and the pillars 10 to connect the pillars 10 to each other. A column connecting portion 20 is provided.
  • a space called a pocket 11 is formed between the pillars 10 adjacent to each other in the circumferential direction.
  • a ball 3 is arranged in each pocket 11 . Therefore, the pillars 10 are interposed between the balls 3 . As a result, contact between the balls 3 is avoided.
  • the pocket 11 is open on one side in the axial direction and closed with the column connecting portion 20 arranged on the other side in the axial direction.
  • the direction in which the pocket 11 is open will be referred to as a first direction X1
  • the direction opposite to the first direction X1 will be referred to as a second direction X2.
  • the column portion 10 is a side surface facing the circumferential direction (toward the pocket 11 ) and has two opposing surfaces 12 that face the rolling surface 3 a of the ball 3 .
  • the two opposing surfaces 12 are a first opposing surface 13 facing the first rotation direction L1 and a second opposing surface 14 facing the second rotation direction.
  • the first opposing surface 13 and the second opposing surface 14 are spherical surfaces in order to reduce sliding resistance with the ball 3 .
  • a pair of claws 15 are provided at the end of the column 10 in the first direction X1. Thereby, the first opposing surface 13 and the second opposing surface 14 are expanded in the first direction X1. Balls 3 are prevented from dropping out of each pocket 11 in the first direction X1. A notch 16 is provided between the pair of claws 15 .
  • the end portion of the column portion 10 in the second direction X2 (hereinafter referred to as the bottom portion 17) is connected to the column connecting portion 20. Therefore, the bottom portions 17 of the column portions 10 and the column connecting portions 20 are alternately arranged in the circumferential direction to form an annular portion 30 .
  • annular portion 30 As shown in FIG. 2, on the side surface of the annular portion 30 in the second direction X2, an annular first rib 31 located radially inward, an annular second rib 32 located radially outward, and an annular planar end surface 33 located between the first rib 31 and the second rib 32 .
  • a recess 35 recessed from the end surface 33 in the first direction X1 is provided in the bottom 17 of the column 10 .
  • the concave portions 35 are arranged at equal intervals in the circumferential direction, and are provided in the same number as the column portions 10 . Therefore, the column portion 10 is hollowed out by the concave portion 35, and the rigidity is lowered.
  • the pillar part 10 is composed of a plurality of walls because the recessed part 35 is provided.
  • the column 10 has a first wall 41 in the first rotation direction L1 when viewed from the recess 35 and a second wall 42 in the second rotation direction L2 when viewed from the recess 35.
  • an inner peripheral wall 43 positioned radially inwardly when viewed from the recess 35
  • an outer peripheral wall 44 (see FIG. 1) positioned radially outwardly viewed from the recess 35
  • a tip wall 45 that
  • the radial thickness H1 of the inner peripheral wall 43 and the radial thickness H2 of the outer peripheral wall 44 are smaller than the radial width H3 of the recess 35 . Therefore, the support rigidity by the inner peripheral wall 43 and the outer peripheral wall 44 is low.
  • the tip wall 45 is the bottom wall of the recess 35 and is positioned in the circumferential direction with respect to the center M of the ball 3 .
  • the axial thickness H4 of the tip wall 45 is substantially the same as the thickness H1 of the inner peripheral wall 43 and the thickness H2 of the outer peripheral wall 44 .
  • the bearing device 80 of Embodiment 1 when the ball 3 is delayed, the ball 3 collides with the first opposing surface 13 (first wall 41). Then, the inner peripheral wall 43, the outer peripheral wall 44, and the tip wall 45 that support the first wall 41 are deformed, and the first wall 41 falls toward the recess 35 (see arrow A in FIG. 3). Therefore, the collision load input to the first wall 41 is absorbed.
  • the bearing device 80 of Embodiment 1 includes the inner ring 1 having the outer circumferential raceway surface 1a on the outer circumferential surface, the outer ring 2 having the inner circumferential raceway surface 2a provided on the inner circumferential surface, the outer circumferential raceway surface 1a and the inner circumferential raceway surface 1a. It has a plurality of balls 3 arranged between the raceway surface 2a and a retainer 4. - ⁇ The retainer 4 is arranged between the inner ring 1 and the outer ring 2, and includes a plurality of column portions 10 provided at regular intervals in the circumferential direction about the axis O of the inner ring 1, and a plurality of column portions 10 connecting the column portions 10 to each other.
  • a pocket 21 in which the ball 3 is arranged is formed between the plurality of pillars 10 .
  • the columnar portion 10 has an end surface 33 facing one of the axial directions parallel to the axis O. As shown in FIG. The end face 33 is provided with a concave portion 35 recessed in the other axial direction.
  • the retainer 4 of the first embodiment suppresses the change in the relative position between the retainer 4 and the balls 3 due to the balls 3 coming into contact with each other. Therefore, fluctuations in torque are suppressed.
  • FIG. 4 is a radial cross-sectional view of the bearing device of Modification 1.
  • FIG. 5 is a perspective view of a retainer of Modification 1.
  • FIG. 4 and 5 a retainer 4A according to Modification 1 is different from the retainer 4 of Embodiment 1 in that openings 36 are provided to open recesses 35 radially inward.
  • the column portion 10A of the retainer 4A of the modified example 1 differs from the retainer 4 of the first embodiment in that it does not have the inner peripheral wall 43 positioned radially inward when viewed from the recess 35 . Therefore, the rigidity of the column portion 10A of Modification 1 is lower than that of the column portion 10 of the first embodiment.
  • the radial length H5 (see FIG. 5) of the tip wall 45A of the column portion 10A of Modification 1 is shorter than the radial length of the tip wall 45 of the first embodiment. Therefore, the rigidity of the column portion 10A is further reduced.
  • the rigidity of the column portion 10A is reduced, and the load that can be absorbed is increased. Therefore, the contact load input to the column portion 10A is reliably absorbed, and torque variation is reliably suppressed.
  • the opening 36 of Modification 1 opens the recess 35 radially inward
  • the present disclosure may be an opening that opens the recess radially outward.
  • FIG. 6 is a radial cross-sectional view of the bearing device of Modification 2.
  • FIG. 7 is a perspective view of a retainer of Modification 2.
  • FIG. 1 the retainer 4B of the bearing device 80B according to Modification 2 differs from the retainer 4B of Embodiment 1 in that the tip end wall 45B is deviated from the ball center M in the first direction X1. 4.
  • the support strength with which the tip wall 45 supports the first wall 41 and the second wall 42 is reduced. Therefore, the amount of deformation of the first wall 41 and the second wall 42 when the ball 3 comes into contact increases (the load that can be absorbed increases), and torque fluctuations are reliably suppressed.
  • the tip wall 45 is moved in the first direction X1. Therefore, the notch amount H6 (see FIG. 6) of the notch 16B is smaller than that of the notch 16 of the first embodiment.
  • FIG. 8 is a perspective view of a retainer of Modification 3.
  • FIG. A retainer 4C of Modified Example 3 differs from the retainer 4 of Embodiment 1 in that through holes 37 are provided through the column portion 10C in the radial direction. Specifically, the cross-sectional shape of the through hole 37 is circular. The through hole 37 penetrates the inner peripheral wall 43 and the outer peripheral wall 44 . Therefore, the recess 35 communicates with the radially inner side and the radially outer side through the through hole 37 .
  • the supporting strength of the inner peripheral wall 43 and the outer peripheral wall 44 supporting the first wall 41 and the second wall 42 is reduced. Therefore, the amount of deformation of the first wall 41 and the second wall 42 when the ball 3 comes into contact increases (the load that can be absorbed increases), and torque fluctuations are reliably suppressed.
  • the present invention is not limited to the above examples.
  • the recess 35 of the embodiment is recessed in the first direction from the bottom 17 of the column 10, but a recess recessed in the second direction X2 is formed on the end face of the tip wall 45 of the column 10 facing the first direction X1. may be provided.
  • Embodiment 2 will be described.
  • FIG. 9 is a side view of the bearing device of Embodiment 2 as seen from one axial direction.
  • 10 is a perspective view of the retainer of Embodiment 2.
  • FIG. 11 is an enlarged view enlarging a part of the bearing device of FIG. 9.
  • FIG. 12 is an enlarged view showing a case where a ball collides with an opposing wall in the bearing device of Embodiment 2.
  • the bearing device 180 includes an annular inner ring 101, an annular outer ring 102 surrounding the outer circumference of the inner ring 101, a plurality of balls 103 arranged between the inner ring 101 and the outer ring 102, and a retainer. 104 and.
  • the direction parallel to the axis O of the inner ring 101 is called the axial direction.
  • One of the rotation directions about the axis O is called a first rotation direction L11, and the opposite direction of the first rotation direction L11 is called a second rotation direction L12.
  • the outer peripheral surface of the inner ring 101 is provided with an outer peripheral raceway surface 101a extending in the circumferential direction.
  • the inner peripheral surface of the outer ring 102 is provided with an inner peripheral raceway surface 102a extending in the circumferential direction.
  • the outer raceway surface 101a and the inner raceway surface 102a face each other in the radial direction.
  • groove shapes of the outer circumference raceway surface 101a and the inner circumference raceway surface 102a are not particularly limited. That is, the outer circumference raceway surface 101a and the inner circumference raceway surface 102a may have either a circular arc shape or a gothic arc shape.
  • the balls 103 are arranged between the outer circumference raceway surface 101a and the inner circumference raceway surface 102a.
  • An outer surface of the ball 103 (hereinafter referred to as a rolling contact surface 103a) is in contact with each of the outer circumference raceway surface 101a and the inner circumference raceway surface 102a.
  • the plurality of balls 103 are arranged around the axis O at regular intervals in the circumferential direction. Thereby, the load acting from the inner ring 101 to the outer ring 102 (or the load acting from the outer ring 102 to the inner ring 101) is evenly distributed in the circumferential direction.
  • the retainer 104 is an annular part made of resin. Note that the present disclosure is not limited to resin retainers. As shown in FIG. 10 , the retainer 104 is arranged between a plurality of holding portions 110 evenly arranged in the circumferential direction around the axis O and the holding portions 110 to connect the holding portions 110 to each other. and a holding portion connection portion 120 .
  • the holding portion 110 has a pair of opposing walls 111 extending in the axial direction and a bottom wall 112 extending in the circumferential direction.
  • the pair of opposing walls 111 are separated from each other in the circumferential direction.
  • the bottom wall 112 connects the axial ends of the two opposing walls 111 . Therefore, when viewed from the radial direction, the holding portion 110 has a U-shape (C-shape) that is open on one side in the axial direction.
  • a space inside the holding portion 110 is called a pocket 113, and the ball 103 is arranged therein.
  • the opposing wall 111 arranged in the first rotation direction L11 as viewed from the pocket 113 is referred to as a first opposing wall 114
  • the opposing wall 111 arranged in the second rotation direction L12 is referred to as a second opposing wall.
  • the first opposing wall 114 has a first opposing surface 114 a facing the pocket 113 and a first outer peripheral surface 114 b facing the direction opposite to the pocket 113 as side surfaces facing the circumferential direction.
  • the second opposing wall 115 has a second opposing surface 115 a facing the pocket 113 and a second outer peripheral surface 115 b facing in the direction opposite to the pocket 113 .
  • the bottom wall 112 has a bottom surface 113a facing the first direction X11 (toward the pocket 113).
  • the bottom surface 113a, the first opposing surface 114a, and the second opposing surface 115a are each spherical in order to reduce sliding resistance with the ball 103. As shown in FIG.
  • the holding portion connecting portion 120 extends in the circumferential direction. An end portion of the holding portion connecting portion 120 in the first rotation direction L11 is connected to the second outer peripheral surface 115b of the second opposing wall 115 . An end portion of the holding portion connecting portion 120 in the second rotation direction L12 is connected to the first outer peripheral surface 114b of the first opposing wall 114 .
  • the axial length N (see FIG. 10) of the holding portion connecting portion 120 is shorter than the axial length of the opposing wall 111 .
  • the holding portion connecting portion 120 connects only a part of the first opposing wall 114 and the second opposing wall 115 in the axial direction, not all of them in the axial direction. Therefore, the rigidity of the holding portion connecting portion 120 is low.
  • the holding portion connecting portion 120 extends linearly in the circumferential direction when viewed from the axial direction.
  • the holding portion connection portion of the present disclosure may have an arc shape when viewed from the axial direction, and is not particularly limited.
  • a virtual line M1 in FIG. 11 is a line passing through the radial center portion of the holding portion connecting portion 120 .
  • the holding portion connecting portion 120 has a substantially trapezoidal shape in which the radially outer side is longer than the radially inner side.
  • a radial thickness H ⁇ b>11 of the holding portion connecting portion 120 is smaller than a radial thickness H ⁇ b>12 of the opposing wall 111 . Therefore, the rigidity of the holding portion connecting portion 120 is low.
  • the holding portion connecting portion 120 is connected to the first outer peripheral surface 114b and the second outer peripheral surface 115b on the radially outer side. That is, the radial central portion of the holding portion connecting portion 120 is arranged radially outward with respect to the virtual circle Q passing through the center of each ball 103 .
  • the holding portion connecting portion 120 moves radially. It receives a load that pushes it outward (see arrow A3 in FIG. 11).
  • the ball 103 when the ball 103 advances or lags in the second embodiment, the ball 103 collides with the first opposing surface 114a (first opposing wall 114) or the second opposing surface 115a (second opposing wall 115). Then, as shown in FIG. 12, the holding portion connecting portion 120 is deformed so as to bend radially outward. Thereby, the collision load input to the first opposing wall 114 or the second opposing wall 115 is absorbed. Therefore, since the rotational speed of cage 104 does not change, the relative position between cage 104 and balls 103 does not change.
  • the bearing device 180 of the second embodiment includes the inner ring 101 having the outer peripheral raceway surface 101a on the outer peripheral surface, the outer ring 102 having the inner peripheral raceway surface 102a provided on the inner peripheral surface, the outer peripheral raceway surface 101a and the inner peripheral raceway surface 101a.
  • a plurality of balls 103 arranged between the raceway surface 102a and a retainer 104 are provided.
  • the retainer 104 has a bottom wall 112 extending in the circumferential direction and a pair of opposing walls 111 extending in the axial direction parallel to the axis O from both circumferential ends of the bottom wall 112 .
  • a space between the pair of opposing walls 111 forms a pocket 113 in which the ball 103 is arranged.
  • the radial thickness H11 of the holding portion connecting portion 120 is smaller than the radial thickness H12 of the opposing wall 111 .
  • the radial center portion of the holding portion connecting portion 120 is arranged radially outward with respect to the virtual circle Q passing through the centers of the balls 103 .
  • the bearing device 180 of the second embodiment even if the balls 103 lead or lag, the relative position between the retainer 104 and the balls 103 is restrained from changing. Therefore, fluctuations in torque are suppressed.
  • FIG. 13 is an enlarged view of the bearing device of Modification 4 as seen from the axial direction.
  • a retainer 104A according to Modification Example 4 differs from the retainer 104 of Embodiment 2 in that it has a retainer connecting portion 120A instead of the retainer connecting portion 120.
  • maintenance part connection parts are arrange
  • the radial thickness of the holding portion connecting portion 120A is the same as the radial thickness H11 (see FIG. 11) of the holding portion connecting portion 120 of the second embodiment, and the radial thickness H12 (see FIG. 11) of the opposing wall 111. 11).
  • the radial center portion of the holding portion connection portion 120 is arranged radially outwardly or radially inwardly with respect to the virtual circle Q passing through the center of each ball 103. It is good if it is.
  • the holding portion connecting portion 120 of the second embodiment is longer in the circumferential direction than the holding portion connecting portion 120A of the modified example 4, and is easily deformed. Therefore, the holding portion connecting portion 120 of Embodiment 2 is more preferable because it can absorb a larger load due to deformation.
  • FIG. 14 is an enlarged view of the bearing device of Modification 5 as seen from the axial direction.
  • a retainer 104B of Modification 5 differs from the retainer 104 of Embodiment 2 in that it has a retainer connecting portion 120B instead of the retainer connecting portion 120 .
  • the holding portion connecting portion 120B overlaps the virtual circle Q when viewed from the axial direction.
  • the radial central portion of the holding portion connecting portion 120B is arranged radially outside of the virtual circle Q.
  • FIG. Therefore, when a circumferential compressive load acts on the holding portion connecting portion 120B, the holding portion connecting portion 120B receives a load that pushes it radially outward and bends radially outward. Therefore, even in the fifth modification, even if the ball 103 advances or lags, the holding portion connection portion 120B is deformed and the contact load of the ball 103 is absorbed. Therefore, as in the second embodiment, torque fluctuations are suppressed.
  • the holding portion connection portion of the present disclosure when viewed from the axial direction parallel to the axis O, it is not essential that the holding portion connection portion does not overlap the virtual circle Q, and the diameter of the holding portion connection portion It is sufficient if the central portion of the direction (see the virtual line M1) is shifted radially outward or inward with respect to the virtual circle Q. However, as the radial center portion of the connecting portion of the holding portion is separated from the virtual circle Q, the amount of bending of the connecting portion of the holding portion increases. Therefore, the holding portion connecting portion 120 of Embodiment 2 is more preferable because it can absorb a larger load due to deformation.
  • FIG. 15 is a perspective view of the retainer of Embodiment 3.
  • FIG. 16 is a cross-sectional view taken along line XVI-XVI of FIG. 15.
  • FIG. 17 is an enlarged view showing a case where a ball collides with an opposing wall in the bearing device of Embodiment 3.
  • the retainer 104C according to the third embodiment differs from the retainer according to the second embodiment in that it has a retainer connecting portion 120C instead of the retainer connecting portion 120.
  • FIG. 15 is a perspective view of the retainer of Embodiment 3.
  • FIG. 16 is a cross-sectional view taken along line XVI-XVI of FIG. 15.
  • FIG. 17 is an enlarged view showing a case where a ball collides with an opposing wall in the bearing device of Embodiment 3.
  • FIG. 15 differs from the retainer according to the second embodiment in that it has a retainer connecting portion 120C instead of the retainer connecting portion 120.
  • the radial thickness H3 of the holding portion connecting portion 120C is the same as the radial thickness H4 of the opposing wall 111 .
  • the radial central portion of the holding portion connecting portion 120 ⁇ /b>C overlaps the virtual circle Q (not shown in FIG. 15 , see FIG. 16 ) connecting the centers of the balls 103 . Therefore, unlike the second embodiment, the holding portion connecting portion 120C does not bend radially outward or radially inward even when subjected to a circumferential compressive load.
  • the holding portion connecting portion 120C is arranged and bent in the second direction X12 from the end portion in the circumferential direction toward the central portion. That is, when viewed from the radial direction, the holding portion connecting portion 120C has a V shape. Therefore, when the holding portion connecting portion 120C receives a compressive load in the circumferential direction, the holding portion connecting portion 120C is deformed so that the bending angle ⁇ of the holding portion connecting portion 120C becomes smaller as shown in FIG. As described above, when the ball 103 advances or lags in Embodiment 3, the holding portion connection portion 120C deforms and the contact load of the ball 103 is absorbed. Therefore, as in the second embodiment, torque fluctuations are suppressed.
  • the holding portion connecting portion 120C of the third embodiment is bent so as to be arranged in the second direction X12 from the end portion in the circumferential direction toward the central portion, but the holding portion connecting portion of the present disclosure is not limited to For example, they may be arranged in the first direction X11, or may be arranged radially inward or radially outward from the ends in the circumferential direction toward the central portion.
  • the bent shape of the holding portion connecting portion of the present disclosure is not limited to a V shape. For example, it may be arc-shaped, U-shaped, or W-shaped. In other words, the connecting portion of the holding portion need not be linear, and is not particularly limited.
  • FIG. 4 is a perspective view of a retainer of Embodiment 4.
  • FIG. A retainer 104D of the fourth embodiment differs from the retainer 104 of the second embodiment in that a retainer connecting portion 120D is provided instead of the retainer connecting portion 120.
  • FIG. The radial thickness of the holding portion connecting portion 120D is the same as the radial thickness H11 (see FIG. 11) of the holding portion connecting portion 120 of the second embodiment. In other words, the radial thickness of the holding portion coupling portion 120D is smaller than the radial thickness H12 of the opposing wall 111 . Further, the holding portion connecting portion 120D is different from the holding portion connecting portion 120 in that it is bent when viewed from the radial direction.
  • the holding portion connecting portion 120D is more easily deformed than the holding portion connecting portion 120 of the second embodiment when receiving a compressive load in the circumferential direction. Specifically, the holding portion connecting portion 120D bends radially outward, and further deforms such that the bending angle of the holding portion connecting portion 120D becomes smaller. As described above, according to the fourth embodiment, a larger contact load can be absorbed, and torque fluctuations are suppressed.
  • FIG. 19 is an enlarged view of the bearing device of Modification 6 viewed from the axial direction.
  • a holding portion connecting portion 120E of a retainer 104E of Modified Example 6 differs from Embodiment 4 in that the bending direction of a holding portion connecting portion 120D is changed. Specifically, the holding portion connecting portion 120E is bent so as to be arranged radially outward from both ends in the circumferential direction toward the central portion. According to Modification 6, as in Embodiment 4, a larger contact load can be absorbed, and torque fluctuations are suppressed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
PCT/JP2022/044221 2021-12-28 2022-11-30 保持器及び軸受装置 Ceased WO2023127384A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP22915615.3A EP4459144A4 (en) 2021-12-28 2022-11-30 RETAINING DEVICE AND LANDING DEVICE
US18/723,014 US20250146529A1 (en) 2021-12-28 2022-11-30 Retainer cage and bearing device
CN202280084108.6A CN118575007A (zh) 2021-12-28 2022-11-30 保持器和轴承装置
JP2023570746A JPWO2023127384A1 (https=) 2021-12-28 2022-11-30

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JP2021-213925 2021-12-28
JP2021213994 2021-12-28
JP2021213925 2021-12-28
JP2021-213994 2021-12-28

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EP (1) EP4459144A4 (https=)
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US3368854A (en) * 1965-12-30 1968-02-13 Federal Mogul Corp Bearing retainer and method of making and assembling same
JP2003287032A (ja) * 2002-03-28 2003-10-10 Nsk Ltd 玉軸受用プラスチック製冠型保持器
JP2004084770A (ja) 2002-08-26 2004-03-18 Nsk Ltd 玉軸受用冠型保持器
JP3985128B2 (ja) 2001-02-15 2007-10-03 株式会社ジェイテクト 転がり軸受用冠型保持器
US20150354630A1 (en) * 2013-01-25 2015-12-10 Aktiebolaget Skf Cage for a rolling bearing, notably for a motor vehicle electric power steering bearing
KR20170095585A (ko) * 2016-02-15 2017-08-23 셰플러코리아(유) 볼 베어링용 케이지

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JP2010071386A (ja) * 2008-09-18 2010-04-02 Ntn Corp 転がり軸受用保持器およびこれを備える転がり軸受
DE102008060760A1 (de) * 2008-12-05 2010-06-10 Schaeffler Kg Kugelkäfig für Radialrillen- oder Schrägkugellager
FR3001510B1 (fr) * 2013-01-25 2016-07-01 Skf Ab Cage pour roulement, notamment pour le roulement de direction electrique de vehicule automobile
WO2015141021A1 (ja) * 2014-03-19 2015-09-24 日本精工株式会社 アンギュラ玉軸受
US10605307B1 (en) * 2018-11-02 2020-03-31 Regal Beloit America, Inc. Bearing retainer, bearing and associated method

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US3368854A (en) * 1965-12-30 1968-02-13 Federal Mogul Corp Bearing retainer and method of making and assembling same
JP3985128B2 (ja) 2001-02-15 2007-10-03 株式会社ジェイテクト 転がり軸受用冠型保持器
JP2003287032A (ja) * 2002-03-28 2003-10-10 Nsk Ltd 玉軸受用プラスチック製冠型保持器
JP2004084770A (ja) 2002-08-26 2004-03-18 Nsk Ltd 玉軸受用冠型保持器
US20150354630A1 (en) * 2013-01-25 2015-12-10 Aktiebolaget Skf Cage for a rolling bearing, notably for a motor vehicle electric power steering bearing
KR20170095585A (ko) * 2016-02-15 2017-08-23 셰플러코리아(유) 볼 베어링용 케이지

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Title
See also references of EP4459144A4

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US20250146529A1 (en) 2025-05-08
EP4459144A1 (en) 2024-11-06
JPWO2023127384A1 (https=) 2023-07-06

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