WO2015141271A1 - 転がり軸受 - Google Patents

転がり軸受 Download PDF

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Publication number
WO2015141271A1
WO2015141271A1 PCT/JP2015/051716 JP2015051716W WO2015141271A1 WO 2015141271 A1 WO2015141271 A1 WO 2015141271A1 JP 2015051716 W JP2015051716 W JP 2015051716W WO 2015141271 A1 WO2015141271 A1 WO 2015141271A1
Authority
WO
WIPO (PCT)
Prior art keywords
slinger
lip
sliding contact
annular
fixed
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/JP2015/051716
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
貴久 中田
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 US15/120,774 priority Critical patent/US9958012B2/en
Priority to CN201580014869.4A priority patent/CN106133355B/zh
Publication of WO2015141271A1 publication Critical patent/WO2015141271A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7859—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element
    • F16C33/7863—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element mounted to the inner race, e.g. a flinger to use centrifugal effect
    • 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
    • F16C19/18—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 two or more rows 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3456—Pressing means without external means for pressing the ring against the face, e.g. slip-ring with a resilient lip
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/346—Pressing means the pressing force varying during operation
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • 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
    • F16C19/08—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 two or more rows 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/63—Gears with belts and pulleys
    • 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
    • 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
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers

Definitions

  • the present invention relates to a rolling bearing provided with a sealing device.
  • pulleys that span endless belts such as timing belts driven by automobile engines and accessory drive belts, such as idler pulleys that adjust the position of endless belts, etc.
  • stationary members such as support shafts by rolling bearings. And is supported rotatably. Since this type of rolling bearing is used in an environment where rainwater, muddy water, or dust easily enters the bearing when the vehicle is running, conventionally, water and dust can be prevented from entering the bearing.
  • a sealing device is incorporated.
  • a sealing device composed of a slinger disposed on the fixed ring (for example, inner ring) side and a seal member disposed on the rotating wheel (for example, outer ring) side is employed.
  • the sealing device is provided in the sealing member, and improves sealing performance by a first lip that is in sliding contact with the fixed ring and a second lip that is in sliding contact with the slinger.
  • this type of rolling bearing although the sealing performance is improved by providing the second lip that is in sliding contact with the slinger, the sliding torque of the bearing increases, and the bearing torque increases when the bearing rotates at high speed. I had a fear. Therefore, this type of rolling bearing is required to reduce bearing torque as well as high sealing performance.
  • Patent Document 1 As a prior art capable of preventing an increase in bearing torque while having high sealing performance, for example, a technique disclosed in Patent Document 1 has been proposed (see FIG. 7).
  • Patent Document 1 in order to prevent an increase in bearing torque, the second lip 201 of the seal member 200 that is in sliding contact with the slinger 100 adopts a lip shape with a narrowed tip, and acts when the outer ring rotates. In consideration of the centrifugal force, the sliding contact width of the second lip 201 with respect to the slinger 100 of the lip tip 202 is changed.
  • the present invention has been made in view of the above-described problems of the prior art, and the problem is to suppress bearing torque and prevent foreign material from entering from the outside, thereby stabilizing the good sealing performance.
  • An object of the present invention is to provide a rolling bearing with high hermeticity that can be exerted.
  • the first invention of the present invention comprises a fixed ring fixed to a stationary member, A rotating wheel disposed relative to the stationary wheel and fixed to the rotating member; A rolling element that is rotatably incorporated between raceways provided on the circumferential surfaces of the fixed ring and the rotating ring that face each other; A sealing device that is provided in an open region at an axial end between the fixed ring and the rotating ring and seals the bearing internal space;
  • the sealing device includes a slinger disposed in an open region of an axial end portion of the fixed wheel, and a seal member disposed in an open region of an axial end portion of the rotating wheel,
  • the slinger includes an annular tube portion that is formed in an annular shape and is fixed to a peripheral surface of a fixed ring, and a disk portion that is integrally formed by projecting radially from the annular tube portion,
  • the seal member is disposed closer to the bearing inner space than the slinger, has a disk-shaped portion with a peripheral edge fixed to the rotating wheel, and is
  • the second lip has an annular projecting portion projecting in the thickness direction at one end portion in the thickness direction of the lip tip portion that is in sliding contact with the slinger, and the thickness of the lip tip portion is set to other than the projecting portion.
  • the projecting portion is formed in a narrower shape toward the distal end side in the thickness direction and constitutes a sliding contact portion that is in sliding contact with the slinger by a line,
  • the slinger is formed such that the disc portion is inclined in the axial direction toward the seal member, and the tip of the disc portion is bent so as to cover the sliding contact portion of the seal member in the axial direction.
  • This is a rolling bearing characterized by integrally forming an annular flange portion.
  • the projecting portion of the lip tip portion of the second lip and the other end portion on the opposite side in the thickness direction are formed in a stepped shape, and the inner peripheral surface of the flange portion of the slinger A labyrinth gap is formed between the two and the rolling bearing.
  • the other end portion of the second lip opposite to the protruding portion of the lip tip in the thickness direction is formed in a stepped shape, and the inner peripheral surface of the flange portion of the slinger This is a rolling bearing characterized by being in sliding contact.
  • the sealing member is formed with an annular flange that protrudes so as to cover the outer peripheral surface of the flange portion of the slinger in the axial direction.
  • This is a rolling bearing characterized by the above.
  • the fixed ring fixed to a stationary member, A rotating wheel disposed relative to the stationary wheel and fixed to the rotating member; A rolling element that is rotatably incorporated between raceways provided on the circumferential surfaces of the fixed ring and the rotating ring that face each other; A sealing device that is provided in an open region at an axial end between the fixed ring and the rotating ring and seals the bearing internal space;
  • the sealing device includes a slinger disposed in an open region of an axial end portion of the fixed wheel, and a seal member disposed in an open region of an axial end portion of the rotating wheel,
  • the slinger includes an annular tube portion that is formed in an annular shape and is fixed to a peripheral surface of a fixed ring, and a disk portion that is integrally formed by projecting radially from the annular tube portion,
  • the seal member is disposed closer to the bearing inner space than the slinger, has a disk-shaped portion with a peripheral edge fixed to the rotating wheel, and is positioned opposite to the peripheral edge fixed to
  • annular first lip that is in sliding contact with the fixed ring
  • annular second lip that protrudes in an inclined manner from an intermediate position of the disk-shaped portion and is in sliding contact with the slinger
  • the second lip is formed with a projecting portion projecting in the thickness direction at one end portion in the thickness direction of the lip tip portion that is in sliding contact with the slinger, and the thickness of the lip tip portion is determined by the projecting portion.
  • the projecting portion is formed in a narrower shape toward the distal end side in the thickness direction and constitutes a sliding contact portion that is in sliding contact with the slinger by a line
  • the slinger is integrally formed with an annular flange portion by bending the tip of the disc portion so as to cover the sliding contact portion of the seal member in the axial direction
  • the disc portion of the slinger is formed in a plurality of stepped shapes by forming a plurality of annular recesses recessed inward in the axial direction in the radial direction of the disc portion. This is a rolling bearing.
  • the second lip is formed in a ring shape with a protruding portion protruding in the thickness direction at one end portion in the thickness direction of the lip tip portion that is in sliding contact with the slinger, and the thickness of the lip tip portion is Since it is formed thicker than the thickness of the lip portion other than the discharge portion, the lip tip portion is easily affected by centrifugal force during high-speed rotation. Therefore, since the second lip is deformed in a direction away from the sliding contact surface with the slinger due to the centrifugal force acting at the time of rotation, the contact force on the sliding contact surface can be reduced.
  • the projecting part is formed so as to narrow toward the tip end in the thickness direction and constitutes a sliding contact part that slides in contact with the slinger with a line.
  • the sliding contact width change with the slinger is suppressed, and a stable sliding contact with a constant width is realized.
  • the disc portion of the slinger is formed to be inclined in the axial direction toward the seal member, and the tip of the disc portion is bent so as to cover the upper portion of the sliding contact portion of the seal member in the axial direction.
  • an annular recess recessed toward the inner side in the axial direction is provided instead of forming the disc portion of the slinger in an inclined shape in the axial direction toward the seal member.
  • an annular recess recessed toward the inner side in the axial direction is provided.
  • FIG. 1 It is a schematic longitudinal cross-sectional view which shows one Embodiment of the rolling bearing apparatus which concerns on this invention.
  • A is a schematic longitudinal cross-sectional view which expands and shows a part of only the sealing device part which comprises the rolling bearing apparatus shown in FIG. 1,
  • (b) is the lip
  • 2nd embodiment of the rolling bearing apparatus which concerns on this invention, Comprising: It is a schematic longitudinal cross-sectional view which expands and shows only a sealing device part partially.
  • FIG. 1 is a schematic longitudinal cross-sectional view which expands and shows a part of only the sealing device part which comprises the rolling bearing apparatus shown in FIG. 1
  • (b) is the lip
  • FIG. 5 is a schematic longitudinal sectional view showing a third embodiment of the rolling bearing device according to the present invention, in which only a sealing device portion is partially enlarged.
  • FIG. 6 is a schematic longitudinal sectional view showing a rolling bearing device according to a fourth embodiment of the present invention, in which only a sealing device portion is partially enlarged.
  • FIG. 10 is a schematic vertical sectional view showing a fifth embodiment of the rolling bearing device according to the present invention, in which only the sealing device portion is partially enlarged. It is a schematic longitudinal cross-sectional view which expands and shows the sealing device part in the conventional rolling bearing apparatus.
  • FIG. 1 is a schematic cross-sectional view in which a first embodiment of a rolling bearing according to the present invention is incorporated in an idler pulley of an automobile.
  • the rolling bearing is arranged coaxially so as to be rotatable relative to the fixed ring 2 and an annular fixed ring (inner ring) 2 provided with a double row inner ring raceway (inner ring raceway groove) 3 continuous in the circumferential direction of the outer peripheral surface.
  • This is a double-row deep groove ball bearing that is provided in an open region at the end of the axial direction indicated by an arrow L1 in the drawing and includes at least a sealing device 17 that seals the bearing internal space 16 (see FIG. 1). ).
  • the inner ring 2 is fixed by fitting a support shaft (not shown) that is a stationary member to the inner peripheral surface, while the outer ring 9 is attached to the inner surface of the pulley that is the rotating member 1.
  • a pulley bearing that is used by rotating the outer ring is assumed in which the outer peripheral surface is fitted and fixed.
  • the sealing device 17 includes a slinger 18 disposed in the open region 8 of the axial end 4 of the inner ring 2 and a seal member 25 disposed in the open region 12 of the axial end 11 of the outer ring 9. (See FIGS. 1 and 2).
  • the slinger 18 is formed in an annular shape as a whole by a metal plate.
  • the slinger 18 includes an annular cylinder portion 19 fitted and fixed to the circumferential surface of the annular small diameter portion 5 formed at the axial end 4 of the inner ring 2, a larger diameter than the annular cylinder portion 19, and from the annular cylinder portion 19. It is composed of a disk portion 20 that is integrally formed so as to protrude in the radial direction (radial direction indicated by arrow L2 in the figure), and is disposed in the open region 8 of the axial end portion 4 of the inner ring 2.
  • the annular tube portion 19 is formed in a cylindrical shape having an inner diameter that can be fitted and fixed to the outer peripheral surface of the annular small-diameter portion 5 of the inner ring 2 by an interference fit (see FIGS. 1 and 2).
  • the disc portion 20 has an outer diameter that is smaller than the inner diameter of the axial end portion 11 of the outer ring 9 and that forms a predetermined gap 21 with the inner diameter of the outer ring 9. Further, the disc portion 20 is formed in an inclined shape in the axial direction toward the seal member direction (the bearing internal direction indicated by the arrow L3 in the figure), and the tip of the disc portion 20 is directed to the seal member direction (the arrow L3 in the figure).
  • the annular flange portion 22 is integrally formed by bending in the bearing internal direction indicated by.
  • the disc portion 20 is formed so as to be inclined in the axial direction toward the seal member direction (the bearing internal direction indicated by arrow L3 in the figure) from the inner diameter side 20a to the outer diameter side 20b (see FIG. 1).
  • the flange portion 22 is substantially parallel to the annular tube portion 19 and is formed so as to protrude in a shorter cylindrical shape than the annular tube portion 19.
  • the flange portion 22 is axially (inner bearing direction indicated by an arrow L3 in the figure).
  • the protruding length of the second lip 46 of the seal member 25, which will be described later, is so long as to cover the lip tip 47 (see FIG. 2).
  • the seal member 25 includes a core metal 26 formed in an annular shape from a metal plate, and a covering portion 32 made of an elastic material such as an elastomer that is integrally formed so as to cover substantially the entire area of the core metal 26.
  • the cored bar 26 has an inner diameter portion 27 formed in a larger diameter toward the outer diameter direction, a disk portion 28 integrally formed from the inner diameter portion 27 toward the outer diameter direction, and an outer portion of the disk portion 28.
  • Annular portion 30 that is integrally bent from the radial end toward the bearing internal direction L3 in the axial direction, and the radial direction (radial direction indicated by arrow L2 in the figure) from the end of the annular portion 30 in the bearing internal direction L3 ), And is formed of a second disk portion 31 that is integrally bent.
  • the inner diameter portion 27 of the core metal 26 is formed to have a larger diameter than the inner peripheral surface of the inner ring 2 (see FIG. 2).
  • the covering portion 32 is integrally formed so as to cover from the inner diameter portion 27 of the core metal 26 to the outer diameter portion of the second disc portion 31.
  • the covering portion 32 is an annular locking groove in which an outer peripheral edge (outer diameter) 33 is formed in a large diameter portion of the inner peripheral surface of the axial end portion 11 of the outer ring 9 closer to the bearing inner space 16 than the slinger 18.
  • 13 is an annular first lip which is located on the inner peripheral edge (inner diameter) 34 opposite to the outer peripheral edge (outer diameter) 33 and in the radial direction (radial direction indicated by the arrow L2 in the figure) and slidably contacts the inner ring 2 (Main lip) 39 is integrally formed.
  • the first lip 39 has an axial direction in a thick portion 37 integrally formed from the end of the disc-shaped portion 35 of the covering portion 32 toward the annular cylindrical portion 19 of the slinger 18 via the thin portion 36. It is formed in a sharp tip shape (in the thickness direction, narrower toward the tip side) that protrudes toward the bearing internal space 16 (in the axial direction indicated by the arrow L1 in the figure), and the axial end of the inner ring 2 In the portion 4, the large diameter portion 6 and the small diameter portion (annular small diameter portion) 5 of the inner ring 2 are slidably contacted (line contact) with a radial wall portion 7 that communicates in a step shape. That is, the sealed area (fourth sealed area 73) formed by sliding contact between the first lip 39 and the radial wall 7 acts to prevent foreign matter from entering the bearing internal space 16.
  • a non-contact annular shape protruding in the shape of a thin flange toward the axial direction opposite to the first lip 39 (axial direction indicated by the arrow L1 in the figure).
  • the auxiliary lip 42 is integrally formed (see FIG. 2A).
  • the non-contact auxiliary lip 42 forms a labyrinth gap 43 with the outer peripheral surface of the annular cylindrical portion 19 of the slinger 18, the sealing region (third sealing region 72) is further increased.
  • the second auxiliary lip 44 projecting annularly in the axial direction opposite to the second lip 46 (axial direction indicated by arrow L1 in the figure) projects integrally. It is formed (see FIG. 2A).
  • the second auxiliary lip 44 is positioned in non-contact with the end of the large diameter portion 6 of the inner ring 2 to form a labyrinth gap 45.
  • the labyrinth gap 45 constitutes a further sealed region (fifth sealed region 74).
  • the second lip 46 expands toward the lip tip 47 (diameter R1 ⁇ R2 when the expansion diameter of the inner diameter side 46a is R1 and the expansion diameter of the outer diameter side 46b is R2). ) So as to protrude in an inclined manner from the outer peripheral surface of the covering portion 32 near the inner peripheral edge 34 and is integrally formed. And the one end part of the thickness direction of the lip front-end
  • the projecting portion 48 is formed so as to narrow toward the tip end in the thickness direction, and constitutes a sliding contact portion 49 that is in sliding contact (line contact) with the slinger 18 by a line. Due to the sealing region (second sealing region 71) of the sliding contact portion 49 between the projecting portion 48 and the slinger 18, foreign matter is introduced into the sealing region (third sealing region 72) by the labyrinth gap 43 between the auxiliary lip 42 and the slinger 18. Works to prevent intrusion.
  • the other end portion 50 located on the opposite side in the thickness direction to the protruding portion 48 of the lip tip 47 in the second lip 46 is formed in a step shape, and the labyrinth between the inner peripheral surface 23 of the flange portion 22 of the slinger 18.
  • a gap 52 is formed (see FIG. 2A). That is, an annular step portion 51 protruding in the radial direction in a step shape is integrally formed at the end portion of the outer diameter surface of the lip tip portion 47 of the second lip 46.
  • the sealing region (first sealing region 70) by the labyrinth gap 52 acts so that foreign matter does not enter the sealing region (second sealing region 71) of the sliding contact portion 49 between the protrusion 48 and the slinger 18.
  • the cross-sectional shape of the annular step portion 51 is formed in a trapezoidal shape, and the tip surface is flat (flat).
  • the second lip 46 is formed with the projecting portion 48 projecting in the thickness direction at the one end portion in the thickness direction of the lip tip portion 47 slidably contacting the slinger 18 in an annular shape. Moreover, since the thickness W2 of the lip tip portion 47 is formed thicker than the thickness W1 of the lip portion other than the protruding portion 48, the lip tip portion 47 is easily affected by centrifugal force during high speed rotation. Accordingly, since the second lip 46 is deformed in a direction away from the sliding contact surface with the slinger 18 due to the centrifugal force acting at the time of rotation, the contact force on the sliding contact surface can be reduced.
  • the projecting portion 48 is formed so as to narrow toward the tip end in the thickness direction and constitutes a sliding contact portion that is in sliding contact with the slinger 18 by a line. Also, the sliding contact width change with the slinger 18 is suppressed, and a stable sliding contact with a constant width is realized. Further, the disc portion 20 of the slinger 18 is formed in an inclined shape in the axial direction toward the seal member direction, and the tip of the disc portion 20 is covered in the axial direction above the sliding contact portion 49 of the seal member 25. By bending and integrally forming the annular flange 22, it is possible to suppress the shape deformation of the slinger 18 and to ensure the accuracy of the slinger falling.
  • the labyrinth gap 52 is provided between the other end portion 50 of the lip tip portion 47 and the inner peripheral surface of the flange portion 22 of the slinger 18, the sealing region 70 is increased, and the protrusion 48 contacting the slinger 18 is used. In addition to the sealed area, foreign substances can be prevented from entering from the outside.
  • FIG. 3 shows a second embodiment of the rolling bearing according to the present invention.
  • the seal member 25 is formed with an annular flange 53 that protrudes so as to cover the outer peripheral surface 24 of the flange portion 22 of the slinger 18 in the axial direction (axial direction indicated by the arrow L1 in the drawing).
  • the flange portion 53 is integrally formed by projecting in an annular shape with a predetermined thickness from the outer diameter side end portion of the disc-shaped portion 35 in the covering portion 32 toward the axial direction (axial direction indicated by arrow L1 in the figure).
  • the flange portion 53 is formed so as to become thinner from the proximal end side 54 toward the distal end side 55, and forms a labyrinth gap 56 with the outer peripheral surface 24 of the flange portion 22 of the slinger 18. That is, according to the present embodiment, the sealing area (sixth sealing area 75) is further increased by the labyrinth gap 56, and the sealing performance is improved.
  • the labyrinth gap 56 is further formed between the inner peripheral surface of the flange portion 53 and the outer peripheral surface of the flange portion 22 of the slinger 18, the sealing region 75 is further increased, and the lip tip Together with the sealing region 70 formed between the other end portion 50 of the portion 47 and the inner peripheral surface of the flange portion 22 of the slinger 18, entry of foreign matter from the outside can be prevented.
  • Other configurations and operational effects are the same as those of the first embodiment.
  • FIG. 4 shows a third embodiment of the rolling bearing according to the present invention.
  • the disk portion 20 of the slinger 18 is not formed in an inclined manner as in the first embodiment, but is an annular recess that is recessed toward the inside in the axial direction (axial direction indicated by the arrow L1 in the figure).
  • 57 is characterized in that it is formed in a plurality of stepped shapes by being formed in a plurality in the radial direction of the disc portion 20 (radial direction indicated by arrow L2 in the figure).
  • the shape and arrangement quantity of the annular recess 57 are not limited and can be appropriately changed within the scope of the present invention. That is, by forming the disc portion 20 of the slinger 18 as in the present embodiment, the rigidity is increased and the tilting in the axial direction is effectively prevented.
  • the disk portion 20 of the slinger 18 has a plurality of steps by forming a plurality of annular recesses 57 that are recessed inward in the axial direction in the radial direction of the disk portion 20. Since it is formed in the attached shape, the shape deformation of the slinger 18 can be suppressed and the falling accuracy of the slinger 18 can be ensured. Other configurations and operational effects are the same as those of the first embodiment.
  • FIG. 5 shows a fourth embodiment of the rolling bearing according to the present invention.
  • the annular step portion 51 protruding in the thickness direction opposite to the protruding portion 48 of the lip tip 47 in the second lip 46 is in sliding contact with the inner peripheral surface 23 of the flange portion 22 of the slinger 18.
  • the shape of the tip sliding contact surface of the annular step portion 51 that is in sliding contact with the inner peripheral surface 23 of the flange portion 22 is formed in an R shape in a sectional view in this embodiment, but the sectional view shown in the embodiment.
  • the trapezoidal shape of the sliding contact surface at the tip can be made flat (flat). According to the present embodiment, since the contact sealing region (seventh sealing region 76) is formed between the tip of the annular step portion 51 and the inner peripheral surface 23 of the flange portion 22, the sealing performance is improved.
  • the sealing region 76 is increased, and the protruding portion 58 in contact with the slinger 18. Together with the sealing region 70, entry of foreign matter from the outside can be prevented.
  • Other configurations and operational effects are the same as those of the first embodiment.
  • FIG. 6 shows a fifth embodiment of the rolling bearing according to the present invention.
  • the flange portion 22 of the slinger 18 has a protruding length that covers the upper portion of the lip tip portion 47 of the second lip 46 in the seal member 25 in the axial direction (axial direction indicated by the arrow L1 in the drawing).
  • One embodiment formed is shown. That is, the bending amount (axial length) of the flange portion 22 is set to be approximately the thickness of the lip tip portion 47.
  • the flange portion of the slinger 18 22 is formed in the axial direction (axial direction indicated by arrow L1 in the drawing) with a protruding length that covers the top of the lip tip portion 47 of the second lip 46 in the seal member 25, so that there is no catch.
  • the foreign matter discharge path 59 can be secured.
  • the accumulated foreign matter can be discharged to the outside by centrifugal force without being caught by the edge of the flange portion 22.
  • the arrow D1 in the figure indicates the foreign substance discharge direction.
  • the rolling bearing of the present invention is not limited to a double-row deep groove ball bearing, and can be applied to other well-known rolling bearings such as a single-row rolling bearing. Further, the rolling elements are not limited to balls, and rollers or the like can be employed. Further, in the present embodiment, the description has been given with the embodiment in which the rolling bearing of the present invention is incorporated in an idler pulley of an automobile. However, for example, the present invention can also be used for a tension pulley used to adjust the tension of an endless belt. The design can be changed as appropriate within the scope of the present invention.
  • Rotating member 2 Fixed ring (inner ring) 3 Inner ring raceway 4 Axial end 8 Open area 9 Rotating wheel (outer ring) DESCRIPTION OF SYMBOLS 10 Outer ring track 11 Axial end part 12 Open area 14 Rolling element 16 Bearing inner space 17 Sealing device 18 Slinger 19 Ring tube part 20 Disk part 22 Flange part 25 Seal member 33 Outer peripheral edge 39 First lip 46 Second lip 47 Lip Tip 48 Projection 49 Sliding part W2 Lip tip thickness W1 Thickness of lip other than protrusion

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
PCT/JP2015/051716 2014-03-19 2015-01-22 転がり軸受 Ceased WO2015141271A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US15/120,774 US9958012B2 (en) 2014-03-19 2015-01-22 Rolling bearing
CN201580014869.4A CN106133355B (zh) 2014-03-19 2015-01-22 滚动轴承

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014057231A JP6439262B2 (ja) 2014-03-19 2014-03-19 転がり軸受
JP2014-057231 2014-03-19

Publications (1)

Publication Number Publication Date
WO2015141271A1 true WO2015141271A1 (ja) 2015-09-24

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Country Status (4)

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US (1) US9958012B2 (enExample)
JP (1) JP6439262B2 (enExample)
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WO (1) WO2015141271A1 (enExample)

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FR3079583B1 (fr) * 2018-04-03 2020-03-06 Aktiebolaget Skf Dispositif de poulie pour galet tendeur ou enrouleur
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US20160363170A1 (en) 2016-12-15
CN106133355A (zh) 2016-11-16
CN106133355B (zh) 2019-04-16
US9958012B2 (en) 2018-05-01
JP2015178881A (ja) 2015-10-08
JP6439262B2 (ja) 2018-12-19

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