WO2022244839A1 - Sealing device - Google Patents

Sealing device Download PDF

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Publication number
WO2022244839A1
WO2022244839A1 PCT/JP2022/020816 JP2022020816W WO2022244839A1 WO 2022244839 A1 WO2022244839 A1 WO 2022244839A1 JP 2022020816 W JP2022020816 W JP 2022020816W WO 2022244839 A1 WO2022244839 A1 WO 2022244839A1
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WO
WIPO (PCT)
Prior art keywords
sealing device
ring
lip
sealing
seal
Prior art date
Application number
PCT/JP2022/020816
Other languages
French (fr)
Japanese (ja)
Inventor
雄一 樽川
一貴 廣田
Original Assignee
Nok株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nok株式会社 filed Critical Nok株式会社
Priority to JP2023522715A priority Critical patent/JPWO2022244839A1/ja
Publication of WO2022244839A1 publication Critical patent/WO2022244839A1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72Sealings
    • F16C33/76Sealings of ball or roller bearings
    • F16C33/78Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/16Sealings between relatively-moving surfaces
    • F16J15/32Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/16Sealings between relatively-moving surfaces
    • F16J15/32Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256Sealings 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

Definitions

  • the present invention relates to a sealing device.
  • the hub of an automobile is equipped with a rolling bearing that supports the axle.
  • This rolling bearing is called a hub bearing.
  • a sealing device is provided between the inner ring and the outer ring of the hub bearing. This sealing device seals lubricant (grease) inside the bearing and prevents foreign substances such as water and dust from entering the bearing from the outside.
  • the inner ring rotating type is a type in which the outer ring is fixed to the vehicle body, and the inner ring and hub fixed to the axle rotate together with the axle. This type is used both when the wheels are driving wheels and when the wheels are driven wheels, as they rotate with the axle.
  • the rotating outer ring type is a type in which the inner ring is fixed to a stationary axle and the outer ring fixed to the wheel rotates together with the wheel. This type is used when the wheel is the driven wheel as the axle is stationary.
  • Some sealing devices provided in hub bearings have a seal member fixed to the outer ring, which is the outer member, and another seal member fixed to the inner ring, which is the inner member. These seal members are brought into slidable contact with each other.
  • the lip of the sealing member that comes into slidable contact with other sealing members is designed to have a large interference margin.
  • the lip interference is designed to be large, the contact pressure of the lip and, in turn, the torque applied to the rotating member will increase.
  • wear of the lip and an increase in temperature due to frictional heat may shorten the life of the sealing device.
  • Sealing devices used in hub bearings with large dimensions have high relative velocities between the inner and outer rings, which increases the risk of lip wear and temperature rise.
  • the present invention provides a sealing device in which the torque applied to the rotating member is small and the temperature rise due to wear of the lip and frictional heat is suppressed.
  • a sealing device is provided between a fixed inner member and a rotating outer member to seal a gap between the inner member and the outer member.
  • the sealing device includes a sleeve attached to the inner member, a first sealing member having a flange extending radially outwardly from the sleeve, and a tubular member disposed radially outwardly of the flange and attached to the outer member.
  • a disc portion extending radially inward from the tubular portion and facing the flange; a radial lip disposed radially inward of the disc portion and slidably contacting the sleeve; a second sealing member having a side lip extending from the portion toward the flange; the side lip of the second seal member slidably contacts the flange when the rotational speed of the outer member is less than a threshold; and when the rotational speed of the outer member is greater than the threshold, Deform away from the flange.
  • the side lips of the second seal member attached to the rotating outer member slidably contact the flange when the rotational speed of the outer member is less than a threshold value to seal the seal. ensure performance.
  • the rotational speed of the outer member is greater than the threshold, the side lip of the second sealing member deforms away from the flange due to the centrifugal force on the side lip itself. Therefore, the torque applied to the rotating outer member is small, and the wear of the side lip and temperature rise due to frictional heat are suppressed.
  • a sealing device is provided between a rotating inner member and a fixed outer member to seal a gap between the inner member and the outer member.
  • the sealing device comprises a first seal member attached to the outer member and a second seal member attached to the inner member.
  • the first seal member has a first rigid ring that is an annular member formed of a rigid material around the axis
  • the second seal member is formed of a rigid material around the axis. It has a second rigid ring, which is an annular member, and a second elastic ring, which is an annular member formed of an elastic material around the axis.
  • the second elastic ring of the second seal member has a side lip that is an annular portion around the axis extending along the axis.
  • the first rigid ring of the first sealing member is contacted by the tip of the side lip.
  • the side lip of the second seal member slidably contacts the first rigid ring of the first seal member and the inner member when the rotation speed of the inner member is less than a threshold value. is greater than a threshold, the first sealing member is deformed to move away from the first rigid ring.
  • FIG. 1 is a partial cross-sectional view of an example of a rolling bearing in which a sealing device according to a first embodiment of the invention is used;
  • FIG. Fig. 4 is a partial cross-sectional view of the sealing device according to the first embodiment of the present invention when the outer member rotates at low speed;
  • FIG. 4 is a partial cross-sectional view of the sealing device according to the first embodiment of the present invention when the outer member rotates at high speed;
  • BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing of an example of the in-wheel motor unit in which the sealing device which concerns on the 1st Embodiment of this invention is used. It is a partial cross-sectional view of a sealing device according to a second embodiment of the present invention.
  • FIG. 5 is a cross-sectional view of a rolling bearing fitted with a sealing device according to a second embodiment of the present invention. It is a partial cross-sectional view of a sealing device according to a third embodiment of the present invention. It is a partial sectional view of the sealing device concerning a 4th embodiment of the present invention.
  • FIG. 1 shows an automobile hub bearing, which is an example of a rolling bearing in which a sealing device according to a first embodiment of the present invention is used.
  • the application of the present invention is not limited to hub bearings, and the present invention can also be applied to other rolling bearings.
  • the hub bearing is a ball bearing, but the application of the invention is not limited to ball bearings, but other rolling bearings, such as roller bearings, needle bearings, etc., having other types of rolling elements.
  • the present invention can also be applied to The present invention can also be applied to rolling bearings used in machines other than automobiles.
  • This hub bearing 1 is of the outer ring rotation type, in which the inner ring is fixed to a stationary axle, and the outer ring fixed to the wheel rotates together with the wheel.
  • the hub bearing 1 includes an inner ring (inner member) 6 having a hole 2 into which an axle is inserted, an outer ring (outer member) 8 arranged outside the inner ring 6, and arranged in a row between the inner ring 6 and the outer ring 8. , a plurality of balls 12 arranged in a row between the inner ring 6 and the outer ring 8, and a plurality of retainers 14, 15 for holding the balls in fixed positions.
  • the inner ring 6 is fixed to a stationary axle.
  • the outer ring 8 serves as a hub fixed to the wheel. Therefore, a hub flange 18 is formed on the outer ring 8 , and a wheel can be attached to the hub flange 18 with hub bolts 19 .
  • the outer ring 8 is fixed to the wheel and rotates with the wheel.
  • the outer ring 8 and the hub flange 18 may be formed as separate members and fixed together.
  • a common center axis Ax of the axle and hub bearing 1 extends vertically in FIG. In FIG. 1, only one portion with respect to the central axis Ax is shown.
  • the lower side of FIG. 1 is the outer side (outboard side) where the wheels of the automobile are arranged
  • the upper side is the inner side (inboard side) where the differential gear and the like are arranged.
  • the outer side and the inner side shown in FIG. 1 mean the radially outer side and the inner side, respectively.
  • a sealing device 20 for sealing the gap between the outer ring 8 and the inner ring 6 is arranged near the cylindrical end portion 8A of the outer ring 8 on the inboard side.
  • the sealing device 20 prevents grease, that is, lubricant from flowing out from the inner space of the hub bearing 1, and foreign matter (including water (including muddy water or salt water) and dust) entering the hub bearing 1 from the outside. Prevent inflow.
  • an arrow F indicates an example of the direction of foreign matter flow from the outside.
  • the sealing device 20 is arranged in the gap between the inboard-side end 8A of the outer ring 8 of the hub bearing 1 and the inner ring 6 of the hub bearing 1 .
  • the sealing device 20 is annular, but only one portion relative to its central axis is shown in FIG.
  • the sealing device 20 has a composite structure comprising a first sealing member 30 and a second sealing member 40. As shown in FIG.
  • the first seal member 30 is a stationary seal member that is fixed to the stationary inner ring 6 and does not rotate.
  • the first sealing member 30 has a rigid ring 31 made of a rigid material such as metal.
  • the rigid ring 31 may be attached with an elastic ring made of an elastic material such as an elastomer.
  • the rigid ring 31 has a substantially L-shaped cross section. Specifically, the rigid ring 31 includes a cylindrical sleeve 31A and an annular flange 31B extending radially outward from the sleeve 31A. A sleeve 31A is attached to the inner ring 6 . Specifically, the end of the inner ring 6 is fitted into the sleeve 31A by an interference fit. Flange 31B is flat and lies in a plane perpendicular to the axis of sleeve 31A. The flange 31B is arranged on the inboard side of the sleeve 31A.
  • the second seal member 40 is a rotary seal member that is fixed to the rotating outer ring 8 and rotates.
  • the second seal member 40 is a composite structure having a resilient ring 41 and a rigid ring 42 .
  • the elastic ring 41 is made of an elastic material such as an elastomer.
  • Rigid ring 42 is made of a rigid material, such as metal, and reinforces elastic ring 41 .
  • Rigid ring 42 has a substantially L-shaped cross-sectional shape. A portion of the rigid ring 42 is embedded in the elastic ring 41 and is in close contact with the elastic ring 41 .
  • the second sealing member 40 has a tubular portion 44 , a disc portion 45 , a grease lip (radial lip) 46 , a seal lip (radial lip) 47 and side lips 48 .
  • the tubular portion 44 is attached to the outer ring 8. Specifically, the tubular portion 44 is fitted into the end portion 8A of the outer ring 8 by an interference fit.
  • the tubular portion 44 is composed of an elastic ring 41 and a rigid ring 42 .
  • the disc portion 45 extends radially inward from the tubular portion 44 and faces the flange 31B of the rigid ring 31 of the first seal member 30 .
  • the disk portion 45 is arranged on the outboard side of the tubular portion 44 .
  • the disc portion 45 is also composed of the elastic ring 41 and the rigid ring 42 .
  • the grease lip 46 and the seal lip 47 are arranged radially inside the disk portion 45 and slidably contact the sleeve 31A.
  • the grease lip 46 and the seal lip 47 are composed of the elastic ring 41 .
  • the grease lip 46 is a thin plate in the shape of a truncated cone or a cylindrical cone extending obliquely from the elastic portion at the radially inner end of the disk portion 45 toward the radially inner side and the outboard side.
  • the tip of the grease lip 46 contacts the outer peripheral surface of the sleeve 31A. The grease lip 46 prevents grease from flowing out from the internal space of the hub bearing 1 to the inboard side.
  • the seal lip 47 is a protrusion formed on the annular portion 49 extending from the elastic portion at the radially inner end of the disk portion 45 toward the inboard side.
  • the annular portion 49 is also composed of the elastic ring 41 . In the initial state when the first sealing member 30 and the second sealing member 40 are not assembled, this ridge has a triangular cross-section shown in phantom lines.
  • the seal lip 47 contacts the outer peripheral surface of the sleeve 31A and backs up the grease lip 46 . In other words, the grease that has passed through the grease lip 46 from the outboard side is prevented from flowing out to the inboard side.
  • a garter spring 50 is wound around the outer circumference of the annular portion 49 .
  • the garter spring 50 exerts a radially inward compressive force on the seal lip 47 to increase the tightening force of the seal lip 47 against the sleeve 31A.
  • the side lip 48 is a thin plate extending from the elastic portion of the disc portion 45 toward the flange 31B.
  • the side lip 48 is composed of the elastic ring 41 .
  • the side lip 48 has a thick base portion 51 adjacent to the disk portion 45, and a thin tip portion 52 extending radially outward from the base portion 51 and obliquely toward the flange 31B and having a truncated cone shape or a conical tubular shape. .
  • the tip portion 52 of the side lip 48 slidably contacts the flange 31B.
  • the tubular portion 44 is arranged further outside the outer edge of the flange 31B of the first seal member 30 .
  • An annular gap 54 is provided between the tubular portion 44 and the flange 31B of the first seal member 30 .
  • Foreign matter may enter the space 55 between the flange 31B of the first seal member 30 and the disk portion 45 of the second seal member 40 through the gap 54 from the outside of the hub bearing 1 . Conversely, foreign matter can be discharged from the space 55 to the outside through the gap 54 .
  • the side lip 48 contacts the flange 31B of the first seal member 30 and enters the space 55. It has the role of preventing foreign matter from further entering toward the seal lip 47 .
  • the time of low speed rotation includes the time when the rotation of the outer ring 8 and the second seal member 40 is stopped.
  • the threshold is, for example, the rotational speed (or number of revolutions), and the threshold may be a constant value or a variable value.
  • the threshold value may change (change over time) with the usage time of the sealing device 20, or may change according to the manner of use such as the ambient temperature of the sealing device 20.
  • the side lip 48 may be coated with grease to reduce the torque imparted to the second seal member 40 from the flange 31B. This grease is different from the grease that typically lubricates the balls 10, 12, outer ring 8 and inner ring 6.
  • the side lip 48 is applied to the side lip 48 itself, as shown in FIG.
  • the centrifugal force deforms the first seal member 30 away from the flange 31B. Therefore, an annular gap 56 is provided between the tip portion 52 of the side lip 48 and the flange 31B.
  • centrifugal force is applied to the second seal member 40 fixed to the outer ring 8 in the sealing device 20 used in the outer ring rotating type hub bearing 1 .
  • the dimensions of the side lip 48 are designed so that the tip 52 is separated from the flange 31B when a large centrifugal force is applied to the side lip 48 .
  • the side lip 48 of the second seal member 40 attached to the rotating outer ring 8 slidably contacts the flange 31B when the rotational speed of the outer ring 8 is less than the threshold value, and the sealing device 20 sealing performance is ensured. That is, the side lip 48 prevents foreign matter that has entered the space 55 from further entering toward the seal lip 47 .
  • FIG. 4 is a diagram illustrating another usage pattern of the sealing device 20 according to the first embodiment of the present invention.
  • the sealing device 20 can also be used, for example, in an in-wheel motor unit as shown in FIG.
  • An in-wheel motor unit is a driving device that is configured by integrating a hub bearing and a motor. , converts the power of the wheels into electric power through a motor generator to generate electricity.
  • the in-wheel motor unit 100 includes an inner ring rotating hub bearing 3, an outer casing 101 as an outer member attached to the hub bearing 3, an inner casing 102 as an inner member, and a motor generator. 103.
  • the outer casing 101 is a tubular member and forms an inner space for housing the hub bearing 3 .
  • the outer casing 101 is sandwiched between a hub flange 18 provided on the inner ring 7 of the hub bearing 3 and a brake disc 110 attached to the hub flange 18 , and by fixing the wheel to the inner ring 7 with hub bolts 19 , the hub flange 18 and the brake disc 110 are attached. It is fixed between the brake disc 110 .
  • the inner casing 102 includes a tubular portion 102a, which is a tubular member forming an inner space for accommodating the outer ring 9 of the hub bearing 3, and a circular portion extending radially outward from the inboard-side end of the tubular portion 102a. It has a disk portion 102b which is a plate-like portion.
  • the cylindrical portion 102a has a shape in which the outer ring 9 is fitted and fixed in the inner space.
  • the outer casing 101 and the inner casing 102 are arranged such that the radially inner surface of the outer casing 101 and the radially outer surface of the cylindrical portion 102a of the inner casing 102 face each other. and the cylindrical portion 102a.
  • the outer casing 101 and the inner casing 102 have an inboard-side end (end 101a) of the outer casing 101 facing the disk portion 102b of the inner casing 102 in the central axis Ax direction. It has a shape that An annular gap is formed between the end portion 101a of the outer casing 101 and the disk portion 102b.
  • the motor generator 103 is a tubular member that extends along the central axis Ax, and is provided in an annular space between the outer casing 101 and the tubular portion 102a of the inner casing 102 .
  • the motor generator 103 includes a rotor 104 and a stator 105.
  • the rotor 104 is fixed to the outer casing 101
  • the stator 105 is fixed to the cylindrical portion 102a of the inner casing 102. .
  • the sealing device 20 prevents foreign matter from entering the in-wheel motor unit 100 through the annular gap between the end portion 101a of the outer casing 101 and the disk portion 102b of the inner casing 102. provided to prevent this.
  • the sealing device 20 is attached between the end portion 101 a of the outer casing 101 and the disk portion 102 b of the inner casing 102 .
  • the sleeve 31A of the first seal member 30 is fitted to the mounting surface 102c of the disc portion 102b of the inner casing 102 by an interference fit, so that the first seal member 30 is mounted on the inner casing 102. It is fixed to the plate portion 102b.
  • the tubular portion 44 of the second seal member 40 is fitted to the mounting surface 101b of the end portion 101a of the outer casing 101 by an interference fit, so that the second seal member 40 is attached to the outer casing 101.
  • the mounting surface 102c of the disk portion 102b of the inner casing 102 is a cylindrical surface extending along the central axis Ax, and the mounting surface 101b of the end portion 101a of the outer casing 101 extends along the central axis Ax. It is an elongated cylindrical surface.
  • the mounting surface 101b and the mounting surface 102c face each other in the radial direction.
  • the sealing device 20 works in the in-wheel motor unit 100 in the same way as when it is attached to the hub bearing 1 described above (see FIG. 3). Specifically, the side lip 48 of the second seal member 40 attached to the rotating outer casing 101 is attached to the flange 31B when the rotation speed of the outer casing 101 and the second seal member 40 is lower than the threshold. The slidable contact ensures the sealing performance of the sealing device 20 . In other words, the side lip 48 prevents foreign matter from entering the space 55 from further entering toward the seal lip 47 .
  • the side lip 48 separates from the flange 31B. An outward air current or centrifugal force is generated, and foreign matter that has entered the space 55 is discharged to the outside through the gap 54 . Also, foreign matter is discharged from the space 57 radially inside the side lip 48 through the gap 56 to the space 55 by airflow or centrifugal force, and is further discharged to the outside through the gap 54 .
  • the sealing device 20 As described above, the torque applied to the rotating outer casing 101 can be reduced when the outer casing 101 rotates at a high speed higher than the threshold. .
  • the outer casing 101 rotates at a high speed higher than the threshold value, it is possible to suppress wear of the side lip 48 and increase in temperature due to frictional heat, thereby suppressing performance degradation and shortening of the life of the sealing device 20. can.
  • the sealing device 20 according to the first embodiment of the present invention can be suitably used also for in-wheel motors.
  • a sealing device 21 according to a second embodiment of the invention differs from the above-described sealing device 20 according to the first embodiment of the present invention in the configuration of the second sealing member. Further, the sealing device 21 according to the second embodiment of the present invention is used for an inner ring rotating type, and is different from the above-described sealing device 20 in terms of application.
  • the same reference numerals are given to the same configurations or configurations having the same functions as those of the sealing device 20, and the description thereof will be omitted, and the different configurations will be described.
  • the annular sealing device 21 includes the first sealing member 30 of the sealing device 20 described above and a second sealing member 60 different from the second sealing member 40 of the sealing device 20. ing.
  • the second seal member 60 has the rigid ring 42 of the second seal member 40 of the sealing device 20 described above. It has a different elastic ring 61 . 5, only one portion of the sealing device 21 with respect to the axis x is shown. In addition, in FIG. 5, the sealing device 21 is shown in a state (arrangement) in use, which will be described later.
  • the elastic ring 61 is made of an elastic material, such as an elastomer, like the elastic ring 41 of the second seal member 40 of the sealing device 20 .
  • the elastic ring 61 is attached to the rigid ring 42 in the same manner as the elastic ring 41 . are embedded in the elastic ring 61 .
  • the elastic ring 61 of the second sealing member 60 as shown in FIG. However, unlike the elastic ring 41 of the second seal member 40 , it does not have a grease lip (radial lip) 46 and a seal lip (radial lip) 47 . Also, unlike the second seal member 40 , the second seal member 60 does not have the annular portion 49 and the garter spring 50 .
  • the side lip 62 has the same shape as the side lip 48 of the second seal member 40, and is part of the thin plate-like elastic ring 61 extending from the elastic portion of the disk portion 45 toward the flange 31B.
  • the side lip 62 has an annular thick base portion 62a adjacent to the disk portion 45, and an annular thin distal end extending radially outward from the base portion 62a and obliquely toward the flange 31B and having a truncated cone shape or a conical cylindrical shape. and a portion 62b.
  • the first sealing member 30 is arranged so as to cover the second sealing member 60 from the outside in the radial direction. Therefore, in use, the second seal member 60 is fixed radially inward of the first seal member 30 .
  • the flange 31B of the first seal member 30 faces the outboard side, and the disk portion 45 of the second seal member 60 faces the inboard side.
  • the tip portion 62b of the side lip 62 slides on the flange 31B.
  • Side lips 62 are designed to allow contact.
  • the side lip 62 deforms and the tip 62b of the side lip 62 moves away from the flange 31B.
  • the side lip 62 is designed to move.
  • the side lip 62 is designed so that the contact between the tip portion 62b of the side lip 62 and the flange 31B is maintained even when the sealing device 21 is applied and the side lip 62 rotates at high speed.
  • annular gap 54 is formed between the tubular portion 44 of the second sealing member 60 and the outer edge 31Bt of the flange 31B of the first sealing member 30, as shown in FIG. is provided. That is, in use, the outboard-side end portion 44a of the tubular portion 44 faces the outer edge 31Bt of the flange 31B with a space therebetween in the radial direction. A gap 54 is formed between it and the outer edge 31Bt. Gap 54 forms a labyrinth seal.
  • an annular gap 63 is provided between the disc portion 45 of the second seal member 60 and the sleeve 31A of the first seal member 30.
  • the outer edge 45a of the disk portion 45 of the second seal member 60 is aligned with the inboard side portion (portion 31Ap) of the sleeve 31A of the first seal member 30.
  • a gap 63 is formed between the outer edge 45a of the disk portion 45 and the portion 31Ap of the sleeve 31A. Gap 63 forms a labyrinth seal.
  • the sealing device 21 is attached to an application and is ready for use.
  • the application target of the sealing device 21 is, for example, a hub bearing, and the hub bearing to which the sealing device 21 is applied is an inner ring rotation type hub bearing.
  • FIG. 6 is a cross-sectional view of the hub bearing 4 to which the sealing device 21 is attached and to which the sealing device 21 is applied.
  • the hub bearing 4 has an inner ring 120 and an outer ring 130. Between the inner ring 120 and the outer ring 130 are a plurality of balls 10 arranged in a row and a plurality of balls 10 arranged in a row. A plurality of balls 12 are provided and a plurality of retainers 14, 15 for holding the balls in place.
  • the inner ring 120 and the outer ring 130 are provided with the balls 10 and 12, which are rolling elements, so that the inner ring 120 and the outer ring 130 are rotatable relative to each other on the same axis indicated by the center axis Ax.
  • the outer ring 130 is fixed to, for example, a suspension system of the vehicle, and the inner ring 120 is rotatable relative to the outer ring 130 .
  • the inner ring 120 has an inner ring 121 and a hub ring 122.
  • the hub ring 122 has a cylindrical shaft portion 123 extending along the center axis Ax and a hub flange 124. ing.
  • the hub flange 124 is a portion extending radially outward from one end of the shaft portion 123 on the outboard side in a disc shape, and is a portion to which wheels (not shown) are attached by a plurality of hub bolts 19 .
  • the inner ring 121 is fitted to the inboard end of the shaft portion 123 of the inner ring 120 to hold the balls 10 and 12 in the space between the inner ring 120 and the outer ring 130 .
  • Outer ring 130 has a through hole 131 extending in the direction of central axis Ax.
  • An annular space extending along the central axis Ax is formed between the shaft portion 123 and the through hole 131 .
  • the balls 10, 12 are accommodated and held by the cages 14, 15 as described above, and a lubricant is applied or injected.
  • a sealing device 21 is attached to an inboard side opening 126 of the hub bearing 4 in which the space between the inner ring 121 and the shaft portion 123 and the through hole 131 forms an opening opened on the inboard side.
  • Another sealing device 140 is attached to an outboard-side opening 127 of the hub bearing 4 in which the space between 121 and the shaft portion 123 and the through hole 131 forms an opening opened on the outboard side.
  • the internal space of the hub bearing 4 is sealed by the sealing devices 21 and 140 to prevent the lubricant in the internal space from leaking to the outside and prevent foreign matter from entering the internal space from the outside. are being prevented.
  • the sealing device 140 is a conventionally known sealing device, and detailed description thereof will be omitted. Note that the sealing device 21 can also be applied as the sealing device 140 .
  • the configuration of the hub bearing to which the sealing device 21 is applied is not limited to the configuration of the hub bearing 4 described above.
  • the sleeve 31A of the first sealing member 30 of the sealing device 21 is attached to the cylindrical end portion 130A on the inboard side of the outer ring 130, and the inboard side of the inner ring 121 of the inner ring 120 is attached.
  • the tubular portion 44 of the second sealing member 60 of the sealing device 21 is attached to the cylindrical end portion 121A, and the sealing device 21 is attached to the hub bearing 4 (see FIG. 5).
  • the sleeve 31A of the first sealing member 30 is fitted into the end portion 130A of the outer ring 130 in an interference fit, and the tubular portion 44 of the second sealing member 60 is specifically fitted to the inner ring.
  • the end portion 121A of 121 is fitted by an interference fit method.
  • the axis x of the sealing device 21 attached to the hub bearing 4 coincides or substantially coincides with the central axis Ax of the hub bearing 4 .
  • the sealing device 21 is fixed to the hub bearing 4 as described above.
  • the first seal member 30 is a stationary seal member that is fixed to the stationary outer ring 130 and does not rotate.
  • the second seal member 60 is a rotary seal member that is fixed to the rotating inner ring 120 and rotates.
  • the sealing device 21 in the hub bearing 4 behaves differently depending on the rotational speed of the inner ring 120 .
  • the side lip 62 is located on the flange of the first seal member 30 as shown in FIG. 31B and has a role of preventing foreign matter from entering the space 55 from further entering the inner space of the hub bearing 4.
  • the time of low speed rotation includes the time when the rotation of the inner ring 120 and the second seal member 60 is stopped.
  • the side lip 62 may be coated with grease to reduce torque applied to the second seal member 60 from the flange 31B. This grease is different from the grease that typically lubricates the balls 10, 12, inner ring 120, and outer ring 130.
  • the side lip 62 when the inner ring 120 and the second seal member 60 rotate at a high speed (when the rotation speed is greater than the threshold value), the side lip 62, particularly the tip portion 62b, moves toward the side lip 62 itself, as indicated by the dotted line in FIG. is deformed away from the flange 31B of the first seal member 30 by the centrifugal force applied to the first seal member 30. As shown in FIG. However, the side lip 62 is designed so that it will not completely separate from the flange 31B due to the centrifugal force applied during high-speed rotation.
  • an annular gap is not provided between the tip portion 62b of the side lip 62 and the flange 31B when the inner ring 120 and the second seal member 60 rotate at high speed. Due to the centrifugal force applied to the side lip 62, the interference between the tip 62b and the flange 31B or the reaction force of the side lip 62 is reduced. Thereby, when the inner ring 120 rotates at high speed, the sliding resistance between the side lip 62 and the flange 31B can be reduced, and the torque applied to the rotating inner ring 120 can be reduced. Also, it is possible to suppress the wear of the side lip 62 and the increase in temperature due to frictional heat.
  • an annular gap 54 is formed between the end portion 44a of the tubular portion 44 of the second seal member 60 and the outer edge 31Bt of the flange 31B of the first seal member 30. provided, the gap 54 functions as a labyrinth seal. Therefore, foreign matter is prevented from entering the internal space of the hub bearing 4 .
  • the labyrinth seal formed by the gap 54 prevents the lubricant from flowing out of the inner space of the hub bearing 4
  • the side lip 62 prevents the lubricant from flowing out of the hub bearing 4 . is prevented.
  • the sealing device 21 can prevent lubricant from flowing out of the internal space of the hub bearing 4 by the gap 54 and the side lip 62 regardless of the rotational speed of the inner ring 120 .
  • an annular gap 63 is formed between the outer edge 45a of the disk portion 45 of the second seal member 60 and the portion Ap of the sleeve 31A of the first seal member 30.
  • the gap 63 functions as a labyrinth seal. Therefore, foreign matter is prevented from entering the space 55 inside the sealing device 21 from the outside of the hub bearing 4 .
  • the sealing device 21 can prevent foreign matter from entering the internal space of the hub bearing 4 by the gap 63 as well.
  • the gap 63 can prevent the lubricant from flowing out of the hub bearing 4 .
  • the side lip 62 of the second seal member 60 attached to the rotating inner ring 120 slidably contacts the flange 31B when the rotational speed of the inner ring 120 is less than the threshold value, thereby closing the sealing device. 21 sealing performance is ensured. That is, during low-speed rotation, the side lip 62 prevents foreign matter from entering the space 55 and further entering the inner space of the hub bearing 4 .
  • the sealing device 21 reduces the torque applied to the rotating inner ring 120 while ensuring sealing performance, and suppresses temperature rise due to wear of the side lip 62 and frictional heat.
  • a sealing device 22 according to a third embodiment of the invention differs from the above-described sealing device 20 according to the first embodiment of the present invention in the configurations of the first sealing member and the second sealing member. Further, the sealing device 22 according to the third embodiment of the present invention is used for an inner ring rotation type application object like the sealing device 21 according to the second embodiment of the present invention. It differs from the sealing device 20 .
  • the same reference numerals are given to the same configurations or configurations having the same functions as those of the sealing device 20, and the description thereof will be omitted, and the different configurations will be described.
  • the annular sealing device 22 has a first sealing member 70 different from the first sealing member 30 of the sealing device 20 described above and a second sealing member 40 of the sealing device 20. and a second sealing member 65 .
  • the first seal member 70 has the rigid ring 42 of the second seal member 30 of the sealing device 20 described above and the elastic ring 71 .
  • the second seal member 65 has the rigid ring 31 of the first seal member 30 of the sealing device 20 described above and the elastic ring 66 . 7, only one portion of the sealing device 22 with respect to the axis x is shown.
  • the sealing device 22 is shown in a state (arrangement) in use, which will be described later.
  • the first sealing member 70 is arranged so as to cover the second sealing member 65 from the outside in the radial direction. Therefore, in use, the second seal member 65 is fixed radially inward of the first seal member 70 .
  • the flange 31B of the second seal member 65 faces the inboard side, and the disk portion 45 of the first seal member 70 faces the outboard side.
  • the elastic ring 71 of the first seal member 70 is made of an elastic material such as an elastomer.
  • the elastic ring 71 is attached to the rigid ring 42 .
  • the elastic ring 71 is in close contact with part of the rigid ring 42 , and part of the rigid ring 42 is attached to the elastic ring 71 .
  • the elastic ring 71 consists of the tubular portion 44 of the elastic ring 41 of the second seal member 40 of the sealing device 20 and the disk portion 45 of the elastic ring 41 of the second seal member 40. It has an inner end portion 72 which is part of the radially inner end, a grease lip 46 and a sealing lip 47 .
  • the elastic ring 71 also has an annular portion 49 of the second seal member 40 extending from the inner end 72 .
  • the first seal member 70 has a garter spring 50 like the second seal member 40 .
  • the grease lip 46 and the seal lip 47 of the second seal member 40 of the sealing device 20 are arranged radially inside the disk portion 45 and slide on the sleeve 31A. configured for movably contact.
  • the grease lip 46 extends from the inner end 72 and the sealing lip 47 is formed on an annular portion 49 extending from the inner end 72 .
  • the elastic ring 71 of the first seal member 70 is not formed in the portion of the disk portion 45 of the first seal member 70 radially outside the inner end portion 72 . Therefore, in the disk portion 45 of the first seal member 70 , a portion radially outside the inner end portion 72 of the rigid ring 42 is exposed, and the rigid ring 42 is radially larger than the inner end portion 72 .
  • a contact surface 73 that is an annular surface facing the inboard side is provided on the portion of the disk portion 45 on the direction outer side.
  • the elastic ring 66 of the second seal member 65 is made of an elastic material such as elastomer.
  • the elastic ring 66 is attached to the rigid ring 31, as shown in FIG. The part is embedded in the elastic ring 66 .
  • the elastic ring 66 of the second seal member 65 is, as shown in FIG. It has a side lip 68 and a labyrinth lip 69 .
  • the base portion 67 extends annularly around the axis x and is formed so as to cover the radially outer end portion of the flange 31B on the radially outer side.
  • the side lip 68 extends from the surface (surface 67a) facing the outboard side of the base portion 67 of the elastic ring 66, and has the same shape as the side lip 48 of the sealing device 20 described above. and is the portion of the thin plate-like elastic ring 66 that extends toward the contact surface 73 of the rigid ring 42 of the first seal member 70 .
  • the side lip 68 has an annular thick base portion 68a adjacent to the base portion 67, and a truncated cone shape or a conical tubular shape extending radially outward from the base portion 68a and obliquely toward the contact surface 73. and an annular thin tip 68b having a shape.
  • the tip 68b of the side lip 68 moves toward the rigid ring.
  • the side lip 68 is designed to slidably contact the contact surface 73 of 42 .
  • the tip portion of the side lip 68 is Side lip 68 is designed such that 68b deforms away from contact surface 73 of rigid ring 42 .
  • the side lip 68 moves away from the contact surface 73 of the rigid ring 42 as long as the tip 68b does not move away from the contact surface 73 of the rigid ring 42. It may be designed to
  • the outer end portion 67b which is the portion of the base portion 67 that covers the radially outer end portion of the flange 31B of the second seal member 65, is located inside the tubular portion 44 of the first seal member 70. It faces a labyrinth receiving portion 71a, which is a portion of the elastic ring 71 at the end on the board side, with a gap in the radial direction. Therefore, a gap 74 is formed between the outer end portion 67 b of the base portion 67 and the labyrinth receiving portion 71 a of the tubular portion 44 .
  • the labyrinth lip 69 extends from the outer end 67b of the base portion 67 toward the labyrinth receiving portion 71a. They are facing each other with a space between them.
  • an annular gap 74a is formed between the tip 69a of the labyrinth lip 69 and the labyrinth receiving portion 71a to further narrow the gap 74.
  • Gap 74 and gap 74a form a labyrinth seal.
  • the sealing device 22 is attached to an application and ready for use.
  • the application target of the sealing device 22 is, for example, a hub bearing, and the hub bearing to which the sealing device 22 is applied is an inner ring rotation type hub bearing.
  • the sealing device 22 is attached, for example, to the hub bearing 4 to which the sealing device 21 described above is attached (see FIG. 6).
  • the illustration of the hub bearing 4 to which the sealing device 22 is attached is omitted.
  • the sealing device 22 is attached to the inboard side opening 126 of the hub bearing 4 in the same manner as the sealing device 21 .
  • the tubular portion 44 of the first sealing member 70 of the sealing device 22 is attached to the inboard side end portion 130A of the outer ring 130, and the inboard side end portion of the inner ring 121 of the inner ring 120 is attached.
  • the sleeve 31A of the second sealing member 65 of the sealing device 22 is attached to 121A, and the sealing device 22 is attached to the hub bearing 4 (see FIGS. 6 and 7).
  • the tubular portion 44 of the first sealing member 70 is specifically fitted to the end portion 130A of the outer ring 130 in an interference fit, and the sleeve 31A of the second sealing member 65 is specifically fitted to the inner ring.
  • the end portion 121A of 121 is fitted by an interference fit method.
  • the axis x of the sealing device 22 attached to the hub bearing 4 coincides or substantially coincides with the central axis Ax of the hub bearing 4 .
  • the sealing device 22 is fixed to the hub bearing 4 as described above.
  • the first seal member 70 is fixed to the stationary outer ring 130 and is a stationary seal member that does not rotate.
  • the second seal member 65 is a rotary seal member that is fixed to the rotating inner ring 120 and rotates.
  • the sealing device 22 in the hub bearing 4 acts differently depending on the rotational speed of the inner ring 120 .
  • the side lip 68 reduces the rigidity of the first seal member 70 as shown in FIG. It contacts the contact surface 73 of the ring 42 and has a role of preventing foreign matter from entering the space 55 from further entering the inner space of the hub bearing 4 .
  • the time of low speed rotation includes the time when the rotation of the inner ring 120 and the second seal member 65 is stopped.
  • the side lip 68 may be coated with grease to reduce the torque imparted to the second seal member 65 from the contact surface 73 of the rigid ring 42 . This grease is different from the grease that typically lubricates the balls 10, 12, inner ring 120, and outer ring 130.
  • annular gaps 74 and 74a are provided between the labyrinth lip 69 of the second seal member 65 and the labyrinth receiving portion 71a of the tubular portion 44 of the first seal member 70.
  • the gaps 74, 74a function as labyrinth seals. Therefore, foreign matter is prevented from entering the space 55 inside the sealing device 22 from the outside of the hub bearing 4 . In this manner, the sealing device 22 can prevent foreign matter from entering the internal space of the hub bearing 4 by the gaps 74 and 74a. In addition, it is possible to prevent the lubricant from flowing out of the hub bearing 4 .
  • the grease lip 46 and the seal lip 47 act similarly to the grease lip 46 and the seal lip 47 of the sealing device 20 described above, respectively. That is, the grease lip 46 prevents the lubricant from flowing out from the inner space of the hub bearing 4 to the inboard side. In addition, the seal lip 47 backs up the grease lip 46 and prevents the lubricant that has passed through the grease lip 46 from flowing out from the outboard side to the inboard side.
  • the grease lip 46 has a shape capable of exhibiting a sufficient clamping force (bonding force) to the sleeve 31A so that the grease lip 46 does not separate from the sleeve 31A when the inner ring 120 of the hub bearing 4 rotates. is preferably formed. This prevents the tip of the grease lip 46 from separating from the sleeve 31A during rotation of the inner ring 120 of the hub bearing 4, particularly during high-speed rotation, and prevents lubricant from leaking from the inner space of the hub bearing 4 to the inboard side. can be suppressed.
  • the garter spring 50 increases the tightening force (tightening force) of the seal lip 47 to the sleeve 31A. It is possible to suppress the leakage of the lubricant to the inboard side.
  • the side lip 68 of the second seal member 65 attached to the rotating inner ring 120 is slidable on the contact surface 73 of the rigid ring 42 when the rotational speed of the inner ring 120 is lower than the threshold. contact to ensure the sealing performance of the sealing device 22 . That is, during low-speed rotation, the side lip 68 prevents foreign matter from entering the space 55 and further entering the inner space of the hub bearing 4 .
  • the sealing device 22 reduces the torque applied to the rotating inner ring 120, and also suppresses wear of the side lip 68 and temperature rise due to frictional heat.
  • a sealing device 23 according to a fourth embodiment of the invention differs from the above-described sealing device 22 according to the third embodiment of the present invention in the configurations of the first sealing member and the second sealing member.
  • the same reference numerals are given to the same configurations or configurations having the same functions as those of the sealing device 22, and the description thereof will be omitted, and the different configurations will be described.
  • the annular sealing device 23 has a first sealing member 75 different from the first sealing member 70 of the sealing device 22 described above and a second sealing member 65 of the sealing device 22. and a second sealing member 80 .
  • the first seal member 75 has the rigid ring 42 of the first seal member 70 of the sealing device 22 described above and an elastic ring 76 different from the elastic ring 71 of the first seal member 70 .
  • the second seal member 80 includes a rigid ring 81 different from the rigid ring 31 of the second seal member 65 of the sealing device 22 described above and an elastic ring 82 different from the elastic ring 66 of the second seal member 65 . and 8, only one portion of the sealing device 23 with respect to the axis x is shown. In addition, in FIG. 8, the sealing device 23 is shown in a state (arrangement) in use, which will be described later.
  • the first sealing member 75 is arranged so as to cover the second sealing member 80 from the outside in the radial direction. Therefore, in use, the second seal member 80 is fixed radially inward of the first seal member 75 . Further, a later-described flange 81B of the second seal member 80 faces the inboard side, and the disk portion 45 of the first seal member 75 faces the outboard side.
  • the elastic ring 76 of the first seal member 75 comprises, as shown in FIG. It differs from the elastic ring 71 of the first sealing member 70 of the sealing device 22 in that it does not have a Therefore, the first seal member 75 does not have the garter spring 50 .
  • the rigid ring 81 of the second sealing member 80 is made of a rigid material, such as metal, and corresponds to the sleeve 31A of the rigid ring 31 of the second sealing member 65 of the sealing device 22, as shown in FIG. It has a sleeve 81A which is a portion and a flange 81B which is a portion corresponding to the flange 31B of the rigid ring 31.
  • the rigid ring 81 has a shape similar to that of the rigid ring 42, and the sleeve 81A has a shape similar to that of the tubular portion 44 of the rigid ring 42, as shown in FIG. 81B has the same shape as the disk portion 45 of the rigid ring 42 .
  • the elastic ring 82 of the second seal member 80 is made of an elastic material such as elastomer.
  • the elastic ring 82 is attached to the rigid ring 81, as shown in FIG. The portion is embedded in the elastic ring 82 .
  • the elastic ring 82 of the second seal member 80 is attached to the outboard side surface of the flange 81B of the rigid ring 81 and the radially outer surface of the sleeve 81A of the rigid ring 81. It has a base 83 which is a portion, and side lips 68 and labyrinth lip 69 which are portions extending from the base 83 .
  • the elastic ring 82 also has a seal projection 84 extending from the base portion 83, as shown in FIG.
  • the base portion 83 extends annularly around the axis x, and is formed so as to cover the radially outer end portion of the flange 81B on the radially outer side, and on the outboard side of the sleeve 81A. is formed to cover the end of the
  • the side lip 68 extends from the surface (surface 83a) facing the outboard side of the base portion 83 of the elastic ring 82, as shown in FIG. It is a portion of a thin plate-like elastic ring 82 that has the same shape as 68 and extends toward the contact surface 73 of the rigid ring 42 of the first sealing member 75 .
  • the side lip 68 has an annular thick base portion 68a adjacent to the base portion 83 and a truncated cone shape or a conical tubular shape extending radially outward from the base portion 68a and obliquely toward the contact surface 73. and an annular thin tip 68b having a shape.
  • the tip portion 68b of the side lip 68 is moved to the rigid ring.
  • the side lip 68 is designed to slidably contact the contact surface 73 of 42 .
  • the tip portion of the side lip 68 is Side lip 68 is designed such that 68b deforms away from contact surface 73 of rigid ring 42 .
  • the side lip 68 moves away from the contact surface 73 of the rigid ring 42 within a range in which the tip portion 68b does not move away from the contact surface 73. It may be designed to
  • the outer end portion 83b which is the portion of the base portion 83 that covers the radially outer end portion of the flange 81B of the second seal member 80, is the elastic portion of the tubular portion 44 of the first seal member 75. It faces the labyrinth receiving portion 71a of the ring 76 with a gap in the radial direction. Therefore, a gap 74 is formed between the outer end portion 83 b of the base portion 83 and the labyrinth receiving portion 71 a of the tubular portion 44 .
  • the labyrinth lip 69 extends from the outer end 83b of the base 83 toward the labyrinth receiving portion 71a. They are facing each other with a space between them.
  • an annular gap 74a is formed between the tip 69a of the labyrinth lip 69 and the labyrinth receiving portion 71a to further narrow the gap 74.
  • Gap 74 and gap 74a form a labyrinth seal.
  • the seal projection 84 is a ring-shaped portion around the axis x, and as shown in FIG. be.
  • the seal projection 84 extends from the outboard side end portion 83 c toward the inner edge 45 b that is the radially inner edge of the disk portion 45 of the rigid ring 42 of the first seal member 75 .
  • the inner edge 45b of the rigid ring 42 is positioned, for example, radially outward and on the outboard side with respect to the outboard side end portion 83c of the base portion 83. extends obliquely from the outboard side end 83c radially outward and toward the outboard side.
  • the sealing projection 84 is formed in such a shape that the tip portion (tip portion 84 a ) of the sealing projection 84 contacts the inner edge 45 b of the rigid ring 42 .
  • the sealing device 23 is attached to the application and is ready for use.
  • the application target of the sealing device 23 is, for example, a hub bearing, and the hub bearing to which the sealing device 23 is applied is an inner ring rotation type hub bearing.
  • the sealing device 23 is mounted, for example, like the sealing device 22, on the hub bearing 4 to which the sealing device 21 described above is mounted (see FIG. 6).
  • the illustration of the hub bearing 4 to which the sealing device 23 is attached is omitted.
  • the sealing device 23 is attached to the inboard side opening 126 of the hub bearing 4 in the same manner as the sealing device 22 . Specifically, the tubular portion 44 of the first sealing member 75 of the sealing device 23 is attached to the inboard side end portion 130A of the outer ring 130, and the inboard side end portion of the inner ring 121 of the inner ring 120 is attached. The sleeve 81A of the second seal member 80 of the sealing device 23 is attached to 121A, and the sealing device 23 is attached to the hub bearing 4 (see FIGS. 6 and 8).
  • the tubular portion 44 of the first sealing member 75 is specifically fitted to the end portion 130A of the outer ring 130 in an interference fit, and the sleeve 81A of the second sealing member 80 is specifically fitted to the inner ring.
  • the end portion 121A of 121 is fitted by an interference fit method.
  • the axis x of the sealing device 23 attached to the hub bearing 4 coincides or substantially coincides with the central axis Ax of the hub bearing 4 .
  • the sealing device 23 is fixed to the hub bearing 4 as described above.
  • the first seal member 75 is a stationary seal member that is fixed to the stationary outer ring 130 and does not rotate.
  • the second seal member 80 is a rotary seal member that is fixed to the rotating inner ring 120 and rotates.
  • the sealing device 23 in the hub bearing 4 acts differently depending on the rotational speed of the inner ring 120 .
  • the side lip 68 of the sealing device 22 and the side lip 68 of the sealing device 22 as shown in FIG. It works similarly to contact the contact surface 73 of the rigid ring 42 of the first seal member 75 to prevent foreign matter from entering the space 55 from further entering the inner space of the hub bearing 4 . It has a deterrent role.
  • the time of low speed rotation includes the time when the rotation of the inner ring 120 and the second seal member 80 is stopped.
  • the side lip 68 may be coated with grease to reduce the torque imparted to the second seal member 80 from the contact surface 73 of the rigid ring 42 . This grease is different from the grease that typically lubricates the balls 10, 12, inner ring 120, and outer ring 130.
  • the side lip 68, particularly the tip portion 68b, of the sealing device 22 as indicated by the dotted line in FIG. Acting like the side lip 68 , the centrifugal force on the side lip 68 itself deforms it away from the contact surface 73 of the rigid ring 42 of the first sealing member 75 . Therefore, similarly to the sealing device 22, when the inner ring 120 and the second sealing member 80 rotate at high speed, the annular gap 56 is formed between the tip portion 68b of the side lip 68 and the contact surface 73 of the rigid ring 42. be provided.
  • annular gaps 74 and 74a are provided between the labyrinth lip 69 of the second seal member 80 and the labyrinth receiving portion 71a of the tubular portion 44 of the first seal member 75. and, like the gaps 74, 74a of the sealing device 22, the gaps 74, 74a function as labyrinth seals. Therefore, foreign matter is prevented from entering the space 55 inside the sealing device 23 from the outside of the hub bearing 4 . In this manner, the sealing device 23 can prevent foreign matter from entering the inner space of the hub bearing 4 by the gaps 74 and 74a. In addition, it is possible to prevent the lubricant from flowing out of the hub bearing 4 .
  • the tip portion 84a of the seal projection 84 is in contact with the inner edge 45b of the rigid ring 42 of the first seal member 75, and the seal projection 84 contacts the inner end of the rigid ring 42 of the first seal member 75. It closes the annular gap between the edge 45b and the outboard side end 83c of the elastic ring 82 of the second seal member 80 . Therefore, the seal projection 84 prevents the lubricant from flowing out from the inner space of the hub bearing 4 to the inboard side. Also, the seal projection 84 prevents foreign matter from entering the internal space of the hub bearing 4 .
  • the tip 84a of the seal projection 84 is in contact with the inner edge 45b of the rigid ring 42 from the inside in the radial direction. Therefore, when the inner ring 120 of the hub bearing 4 rotates and a centrifugal force is applied to the seal projection 84 , the distal end portion 84 a of the seal projection 84 is further pressed against the inner edge 45 b of the rigid ring 42 . Therefore, when the inner ring 120 of the hub bearing 4 rotates, particularly during high-speed rotation, it is possible to prevent the tip 84a of the seal projection 84 from separating from the inner edge 45b of the rigid ring 42. The leakage of the lubricant to the side can be further suppressed.
  • the side lip 68 of the second seal member 80 attached to the rotating inner ring 120 is slidable on the contact surface 73 of the rigid ring 42 when the rotational speed of the inner ring 120 is less than the threshold. to ensure the sealing performance of the sealing device 23. That is, during low-speed rotation, the side lip 68 prevents foreign matter from entering the space 55 and further entering the inner space of the hub bearing 4 .
  • the sealing device 23 reduces the torque applied to the rotating inner ring 120, and suppresses temperature rise due to wear of the side lip 68 and frictional heat.
  • the rotational speed thresholds of the hub bearings 1, 3, 4 at which the side lips 48, 62, 68 are deformed at high speeds are, for example, It can be adjusted by the shape of 52, 62b, 68b, the characteristics of the elastic material of the elastic rings 41, 61, 66, 82, and the like.
  • the shapes of the base portions 51, 62a, 68a and the tip portions 52, 62b, 68b include, for example, the thickness and hardness of the base portions 51, 62a, 68a and the tip portions 52, 62b, 68b.
  • Properties of the elastic material include, for example, the elastic modulus of the elastic material.
  • the threshold values of the rotational speeds of the hub bearings 1, 3, 4 at which the side lips 48, 62, 68 are respectively deformed during high-speed rotation are the first seal members 30, 70, 75 and the second It can also be adjusted by the distance (interval) to the seal members 40 , 60 , 65 , 80 .
  • multiple side lips may be provided.
  • a protrusion may be provided in the space 55 to reduce the entry of foreign matter into the side lips 48, 62, 68.
  • the protrusions may be formed on the first sealing members 30, 70, 75 or may be formed on the second sealing members 40, 60, 65.
  • Garter spring 51, 62a, 68a... Base part, 52, 62b, 68b... Tip part, 54, 63, 74, 74a... Gap 67, 83... Base part 67a, 83a... Surface 67b, 83b... Outer end part 69... Labyrinth lip 69a... Tip part 71, 76... Elastic ring 71a... Labyrinth receiving part , 72... Inner end 73... Contact surface 83c... Outboard side end 84... Seal projection 84a... Tip part 100... In-wheel motor unit 101... Outer casing 101a... End 101b... Mounting Surface 102... Inner casing 102a... Cylindrical part 102b... Disk part 102c...
  • Mounting surface 103 Motor generator 104
  • Rotor 105 Stator 110
  • Brake disc 121 Inner ring 121A... End , 122...Hub ring, 123...Axle, 124...Hub flange, 126...Inboard side opening, 127...Outboard side opening, 130A...End, 131...Through hole, 140...Other sealing device, Ax ... central axis, x ... axis

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

Provided is a sealing device in which a torque applied to a rotating member is small and in which the wear of lips and a temperature rise due to frictional heat are suppressed. A sealing device (20) is disposed between a fixed inner-side member and a rotating outer-side member to seal a gap between the inner-side member and the outer-side member. A first sealing member (30) of the sealing device (20) has a sleeve (31A) mounted to the inner-side member and a flange (31B) expanding radially outward from the sleeve (31A). A second sealing member (40) of the sealing device (20) has a tubular portion (44) disposed on the radially outer side of the flange and mounted to the outer-side member, a disc portion (45) expanding radially inward from the tubular portion (44) and opposed to the flange (31B), radial lips (46, 47) disposed on the radially inner side of the disc portion (45) in slidable contact with the sleeve (31A), and a side lip (48) extending from the disc portion (45) toward the flange (31B). The side lip (48) of the second sealing member (40) is brought into slidable contact with the flange (31B) when the rotational speed of the outer-side member is lower than a threshold value and is deformed so as to be apart from the flange (31B) when the rotational speed of the outer-side member is higher than the threshold value.

Description

密封装置sealing device
 本発明は、密封装置に関する。 The present invention relates to a sealing device.
 自動車のハブには、車軸を支持する転がり軸受が設けられる。この転がり軸受をハブベアリングと呼ぶ。ハブベアリングの内輪と外輪の間には密封装置が設けられる。この密封装置は、軸受内部の潤滑剤(グリース)を密封するとともに、外部から水やダスト等の異物が軸受内部へ侵入しないように阻止する。 The hub of an automobile is equipped with a rolling bearing that supports the axle. This rolling bearing is called a hub bearing. A sealing device is provided between the inner ring and the outer ring of the hub bearing. This sealing device seals lubricant (grease) inside the bearing and prevents foreign substances such as water and dust from entering the bearing from the outside.
 ハブベアリングには、内輪回転型と外輪回転型がある(特許文献1)。内輪回転型は、外輪が車体に固定されており、車軸に固定される内輪とハブが車軸とともに回転するタイプである。このタイプは、車輪が車軸とともに回転するので、車輪が駆動輪である場合にも、車輪が従動輪である場合にも使用される。外輪回転型は、静止した車軸に内輪が固定され、車輪に固定される外輪が車輪とともに回転するタイプである。このタイプは、車軸が静止しているので、車輪が従動輪である場合に使用される。 There are two types of hub bearings: inner ring rotating type and outer ring rotating type (Patent Document 1). The inner ring rotating type is a type in which the outer ring is fixed to the vehicle body, and the inner ring and hub fixed to the axle rotate together with the axle. This type is used both when the wheels are driving wheels and when the wheels are driven wheels, as they rotate with the axle. The rotating outer ring type is a type in which the inner ring is fixed to a stationary axle and the outer ring fixed to the wheel rotates together with the wheel. This type is used when the wheel is the driven wheel as the axle is stationary.
国際公開第2015/182357号WO2015/182357
 ハブベアリングに設けられる密封装置は、外側部材である外輪に固定されるシール部材と、内側部材である内輪に固定されるもう1つのシール部材を有するものがある。これらのシール部材は、互いに摺動可能に接触させられる。 Some sealing devices provided in hub bearings have a seal member fixed to the outer ring, which is the outer member, and another seal member fixed to the inner ring, which is the inner member. These seal members are brought into slidable contact with each other.
 一般的には、ハブベアリングに設けられる密封装置の封止性能を確保するために、他のシール部材に摺動可能に接触するシール部材のリップの締め代が大きく設計されている。しかし、リップの締め代を大きく設計すると、リップの接触圧、ひいては回転する部材にかかるトルクが大きくなる。また、リップの摩耗、摩擦熱による温度の上昇が密封装置の寿命の低下を引き起こすおそれがある。寸法が大きいハブベアリングに使用される密封装置では、内輪と外輪の相対速度が大きく、リップの摩耗および温度上昇のおそれが大きい。 In general, in order to ensure the sealing performance of the sealing device provided in the hub bearing, the lip of the sealing member that comes into slidable contact with other sealing members is designed to have a large interference margin. However, if the lip interference is designed to be large, the contact pressure of the lip and, in turn, the torque applied to the rotating member will increase. In addition, wear of the lip and an increase in temperature due to frictional heat may shorten the life of the sealing device. Sealing devices used in hub bearings with large dimensions have high relative velocities between the inner and outer rings, which increases the risk of lip wear and temperature rise.
 そこで、本発明は、回転する部材にかかるトルクが小さく、リップの摩耗、摩擦熱による温度の上昇が抑制される密封装置を提供する。 Therefore, the present invention provides a sealing device in which the torque applied to the rotating member is small and the temperature rise due to wear of the lip and frictional heat is suppressed.
 本発明のある態様によれば、固定された内側部材と回転する外側部材との間に配置され、前記内側部材と前記外側部材との間の間隙を封止する密封装置が提供される。密封装置は、前記内側部材に取り付けられたスリーブと、前記スリーブから径方向外側に広がるフランジを有する第1のシール部材と、前記フランジの径方向外側に配置されて前記外側部材に取り付けられた管状部と、前記管状部から径方向内側に広がり前記フランジに対向する円板部と、前記円板部の径方向内側に配置されて前記スリーブに摺動可能に接触するラジアルリップと、前記円板部から前記フランジに向けて延びるサイドリップを有する第2のシール部材を有する。前記第2のシール部材の前記サイドリップは、前記外側部材の回転速度が閾値より小さい場合には、前記フランジに摺動可能に接触し、前記外側部材の回転速度が閾値より大きい場合には、前記フランジから離れるよう変形する。 According to one aspect of the invention, a sealing device is provided between a fixed inner member and a rotating outer member to seal a gap between the inner member and the outer member. The sealing device includes a sleeve attached to the inner member, a first sealing member having a flange extending radially outwardly from the sleeve, and a tubular member disposed radially outwardly of the flange and attached to the outer member. a disc portion extending radially inward from the tubular portion and facing the flange; a radial lip disposed radially inward of the disc portion and slidably contacting the sleeve; a second sealing member having a side lip extending from the portion toward the flange; the side lip of the second seal member slidably contacts the flange when the rotational speed of the outer member is less than a threshold; and when the rotational speed of the outer member is greater than the threshold, Deform away from the flange.
 この態様においては、回転する外側部材に取り付けられた第2のシール部材のサイドリップは、外側部材の回転速度が閾値より小さい場合には、フランジに摺動可能に接触し、密封装置の封止性能を確保する。一方、外側部材の回転速度が閾値より大きい場合には、第2のシール部材のサイドリップは、サイドリップ自身にかかる遠心力によって、フランジから離れるよう変形する。したがって、回転する外側部材にかかるトルクが小さく、サイドリップの摩耗、摩擦熱による温度の上昇が抑制される。 In this aspect, the side lips of the second seal member attached to the rotating outer member slidably contact the flange when the rotational speed of the outer member is less than a threshold value to seal the seal. ensure performance. On the other hand, when the rotational speed of the outer member is greater than the threshold, the side lip of the second sealing member deforms away from the flange due to the centrifugal force on the side lip itself. Therefore, the torque applied to the rotating outer member is small, and the wear of the side lip and temperature rise due to frictional heat are suppressed.
 本発明のある態様によれば、回転する内側部材と固定された外側部材との間に配置され、前記内側部材と前記外側部材との間の間隙を封止する密封装置が提供される。密封装置は、前記外側部材に取り付けられる第1のシール部材と、前記内側部材に取り付けられる第2のシール部材とを備える。前記第1のシール部材は、剛性材料から形成された軸線周りに環状の部材である第1の剛性環を有しており、前記第2のシール部材は、剛性材料から形成された前記軸線周りに環状の部材である第2の剛性環と、弾性材料から形成された前記軸線周りに環状の部材である第2の弾性環とを有している。前記第2のシール部材の前記第2の弾性環は、前記軸線に沿って延びる前記軸線周りに環状の部分であるサイドリップを有している。前記第1のシール部材の前記第1の剛性環は、前記サイドリップの先端部が接触するようになっている。前記第2のシール部材の前記サイドリップは、前記内側部材の回転速度が閾値より小さい場合には、前記第1のシール部材の前記第1の剛性環に摺動可能に接触し、前記内側部材の回転速度が閾値より大きい場合には、前記第1のシール部材の前記第1の剛性環から離れる方向に移動するよう変形する。 According to one aspect of the invention, a sealing device is provided between a rotating inner member and a fixed outer member to seal a gap between the inner member and the outer member. The sealing device comprises a first seal member attached to the outer member and a second seal member attached to the inner member. The first seal member has a first rigid ring that is an annular member formed of a rigid material around the axis, and the second seal member is formed of a rigid material around the axis. It has a second rigid ring, which is an annular member, and a second elastic ring, which is an annular member formed of an elastic material around the axis. The second elastic ring of the second seal member has a side lip that is an annular portion around the axis extending along the axis. The first rigid ring of the first sealing member is contacted by the tip of the side lip. The side lip of the second seal member slidably contacts the first rigid ring of the first seal member and the inner member when the rotation speed of the inner member is less than a threshold value. is greater than a threshold, the first sealing member is deformed to move away from the first rigid ring.
本発明の第1の実施形態に係る密封装置が使用される転がり軸受の一例の部分断面図である。1 is a partial cross-sectional view of an example of a rolling bearing in which a sealing device according to a first embodiment of the invention is used; FIG. 外側部材が低速で回転する時の本発明の第1の実施形態に係る密封装置の部分断面図である。Fig. 4 is a partial cross-sectional view of the sealing device according to the first embodiment of the present invention when the outer member rotates at low speed; 外側部材が高速で回転する時の本発明の第1の実施形態に係る密封装置の部分断面図である。FIG. 4 is a partial cross-sectional view of the sealing device according to the first embodiment of the present invention when the outer member rotates at high speed; 本発明の第1の実施形態に係る密封装置が使用されるインホイールモータユニットの一例の断面図である。BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing of an example of the in-wheel motor unit in which the sealing device which concerns on the 1st Embodiment of this invention is used. 本発明の第2の実施形態に係る密封装置の部分断面図である。It is a partial cross-sectional view of a sealing device according to a second embodiment of the present invention. 本発明の第2の実施形態に係る密封装置が取り付けられた転がり軸受の断面図である。FIG. 5 is a cross-sectional view of a rolling bearing fitted with a sealing device according to a second embodiment of the present invention; 本発明の第3の実施形態に係る密封装置の部分断面図である。It is a partial cross-sectional view of a sealing device according to a third embodiment of the present invention. 本発明の第4の実施形態に係る密封装置の部分断面図である。It is a partial sectional view of the sealing device concerning a 4th embodiment of the present invention.
 以下、添付の図面を参照しながら本発明に係る実施の形態を説明する。図面の縮尺は必ずしも正確ではなく、一部の特徴は誇張または省略されることもある。 Hereinafter, embodiments according to the present invention will be described with reference to the accompanying drawings. The drawings are not necessarily drawn to scale and some features may be exaggerated or omitted.
 図1は、本発明の第1の実施形態に係る密封装置が使用される転がり軸受の一例である自動車用のハブベアリングを示す。但し、本発明の用途はハブベアリングには限定されず、他の転がり軸受にも本発明は適用可能である。また、以下の説明では、ハブベアリングは、玉軸受であるが、本発明の用途は玉軸受には限定されず、他の種類の転動体を有する、ころ軸受、針軸受などの他の転がり軸受にも本発明は適用可能である。また、自動車以外の機械に使用される転がり軸受にも本発明は適用可能である。 FIG. 1 shows an automobile hub bearing, which is an example of a rolling bearing in which a sealing device according to a first embodiment of the present invention is used. However, the application of the present invention is not limited to hub bearings, and the present invention can also be applied to other rolling bearings. Also, in the following description, the hub bearing is a ball bearing, but the application of the invention is not limited to ball bearings, but other rolling bearings, such as roller bearings, needle bearings, etc., having other types of rolling elements. The present invention can also be applied to The present invention can also be applied to rolling bearings used in machines other than automobiles.
 このハブベアリング1は、外輪回転型であり、静止した車軸に内輪が固定され、車輪に固定される外輪が車輪とともに回転する。ハブベアリング1は、車軸が挿入される孔2を有する内輪(内側部材)6と、内輪6の外側に配置された外輪(外側部材)8と、内輪6と外輪8の間に1列に配置された複数の玉10と、内輪6と外輪8の間に1列に配置された複数の玉12と、これらの玉を定位置に保持する複数の保持器14,15を有する。 This hub bearing 1 is of the outer ring rotation type, in which the inner ring is fixed to a stationary axle, and the outer ring fixed to the wheel rotates together with the wheel. The hub bearing 1 includes an inner ring (inner member) 6 having a hole 2 into which an axle is inserted, an outer ring (outer member) 8 arranged outside the inner ring 6, and arranged in a row between the inner ring 6 and the outer ring 8. , a plurality of balls 12 arranged in a row between the inner ring 6 and the outer ring 8, and a plurality of retainers 14, 15 for holding the balls in fixed positions.
 内輪6は静止した車軸に固定されている。外輪8は、車輪に固定されるハブの役割を有する。したがって、外輪8には、ハブフランジ18が形成されおり、ハブフランジ18には、ハブボルト19によって、車輪を取り付けることができる。このように、外輪8は、車輪に固定されて車輪とともに回転する。但し、外輪8とハブフランジ18を別個の部材として形成し、これらを固定してもよい。 The inner ring 6 is fixed to a stationary axle. The outer ring 8 serves as a hub fixed to the wheel. Therefore, a hub flange 18 is formed on the outer ring 8 , and a wheel can be attached to the hub flange 18 with hub bolts 19 . Thus, the outer ring 8 is fixed to the wheel and rotates with the wheel. However, the outer ring 8 and the hub flange 18 may be formed as separate members and fixed together.
 車軸およびハブベアリング1の共通の中心軸線Axは、図1の上下方向に延びている。図1においては、中心軸線Axに対する一方の部分のみが示されている。詳細には図示しないが、図1の下側は自動車の車輪が配置される外側(アウトボード側)であり、上側は差動歯車などが配置される内側(インボード側)である。図1に示した外側、内側は、それぞれ径方向の外側、内側を意味する。 A common center axis Ax of the axle and hub bearing 1 extends vertically in FIG. In FIG. 1, only one portion with respect to the central axis Ax is shown. Although not shown in detail, the lower side of FIG. 1 is the outer side (outboard side) where the wheels of the automobile are arranged, and the upper side is the inner side (inboard side) where the differential gear and the like are arranged. The outer side and the inner side shown in FIG. 1 mean the radially outer side and the inner side, respectively.
 外輪8のインボード側の円筒状の端部8Aの付近には、外輪8と内輪6の間の間隙を封止する密封装置20が配置されている。密封装置20は、ハブベアリング1の内部空間からのグリース、すなわち潤滑剤の流出を防止するとともに、外部からハブベアリング1の内部への異物(水(泥水または塩水を含む)およびダストを含む)の流入を防止する。図1において、矢印Fは、外部からの異物の流れの方向の例を示す。 A sealing device 20 for sealing the gap between the outer ring 8 and the inner ring 6 is arranged near the cylindrical end portion 8A of the outer ring 8 on the inboard side. The sealing device 20 prevents grease, that is, lubricant from flowing out from the inner space of the hub bearing 1, and foreign matter (including water (including muddy water or salt water) and dust) entering the hub bearing 1 from the outside. Prevent inflow. In FIG. 1, an arrow F indicates an example of the direction of foreign matter flow from the outside.
 図2に示すように、密封装置20は、ハブベアリング1の外輪8のインボード側の端部8Aと、ハブベアリング1の内輪6との間隙内に配置される。密封装置20は環状であるが、図2においては、その中心軸線に対する一方の部分のみが示されている。図2から明らかなように、密封装置20は、第1のシール部材30と第2のシール部材40を備える複合構造を有する。 As shown in FIG. 2 , the sealing device 20 is arranged in the gap between the inboard-side end 8A of the outer ring 8 of the hub bearing 1 and the inner ring 6 of the hub bearing 1 . The sealing device 20 is annular, but only one portion relative to its central axis is shown in FIG. As can be seen from FIG. 2, the sealing device 20 has a composite structure comprising a first sealing member 30 and a second sealing member 40. As shown in FIG.
 第1のシール部材30は、静止した内輪6に固定され、回転しない固定シール部材である。第1のシール部材30は、剛性材料、例えば金属から形成された剛性環31を有する。図示しないが、剛性環31に、弾性材料、例えばエラストマーで形成された弾性環を取り付けてもよい。 The first seal member 30 is a stationary seal member that is fixed to the stationary inner ring 6 and does not rotate. The first sealing member 30 has a rigid ring 31 made of a rigid material such as metal. Although not shown, the rigid ring 31 may be attached with an elastic ring made of an elastic material such as an elastomer.
 剛性環31は、ほぼL字形の断面形状を有する。具体的には、剛性環31は、円筒状のスリーブ31Aと、スリーブ31Aから径方向外側に広がる円環状のフランジ31Bを備える。スリーブ31Aは内輪6に取り付けられる。具体的には、スリーブ31Aには、内輪6の端部が締まり嵌め方式で嵌め入れられる。フランジ31Bは平板であり、スリーブ31Aの軸線に対して垂直な平面内にある。フランジ31Bはスリーブ31Aのインボード側に配置されている。 The rigid ring 31 has a substantially L-shaped cross section. Specifically, the rigid ring 31 includes a cylindrical sleeve 31A and an annular flange 31B extending radially outward from the sleeve 31A. A sleeve 31A is attached to the inner ring 6 . Specifically, the end of the inner ring 6 is fitted into the sleeve 31A by an interference fit. Flange 31B is flat and lies in a plane perpendicular to the axis of sleeve 31A. The flange 31B is arranged on the inboard side of the sleeve 31A.
 第2のシール部材40は、回転する外輪8に固定され、回転する回転シール部材である。第2のシール部材40は、弾性環41および剛性環42を有する複合構造である。弾性環41は、弾性材料、例えばエラストマーで形成されている。剛性環42は、剛性材料、例えば金属から形成されており、弾性環41を補強する。剛性環42は、ほぼL字形の断面形状を有する。剛性環42の一部は、弾性環41に埋設されており、弾性環41に密着している。 The second seal member 40 is a rotary seal member that is fixed to the rotating outer ring 8 and rotates. The second seal member 40 is a composite structure having a resilient ring 41 and a rigid ring 42 . The elastic ring 41 is made of an elastic material such as an elastomer. Rigid ring 42 is made of a rigid material, such as metal, and reinforces elastic ring 41 . Rigid ring 42 has a substantially L-shaped cross-sectional shape. A portion of the rigid ring 42 is embedded in the elastic ring 41 and is in close contact with the elastic ring 41 .
 第2のシール部材40は、管状部44、円板部45、グリースリップ(ラジアルリップ)46、シールリップ(ラジアルリップ)47およびサイドリップ48を有する。 The second sealing member 40 has a tubular portion 44 , a disc portion 45 , a grease lip (radial lip) 46 , a seal lip (radial lip) 47 and side lips 48 .
 管状部44は外輪8に取り付けられる。具体的には、管状部44は外輪8の端部8Aに締まり嵌め方式で嵌め入れられる。管状部44は、弾性環41と剛性環42から構成されている。 The tubular portion 44 is attached to the outer ring 8. Specifically, the tubular portion 44 is fitted into the end portion 8A of the outer ring 8 by an interference fit. The tubular portion 44 is composed of an elastic ring 41 and a rigid ring 42 .
 円板部45は、管状部44から径方向内側に広がり、第1のシール部材30の剛性環31のフランジ31Bに対向する。円板部45は管状部44のアウトボード側に配置されている。円板部45も、弾性環41と剛性環42から構成されている。 The disc portion 45 extends radially inward from the tubular portion 44 and faces the flange 31B of the rigid ring 31 of the first seal member 30 . The disk portion 45 is arranged on the outboard side of the tubular portion 44 . The disc portion 45 is also composed of the elastic ring 41 and the rigid ring 42 .
 グリースリップ46とシールリップ47は、円板部45の径方向内側に配置されてスリーブ31Aに摺動可能に接触する。グリースリップ46とシールリップ47は、弾性環41から構成されている。 The grease lip 46 and the seal lip 47 are arranged radially inside the disk portion 45 and slidably contact the sleeve 31A. The grease lip 46 and the seal lip 47 are composed of the elastic ring 41 .
 外輪8と内輪6の間において、円板部45のアウトボード側の空間(ハブベアリング1の内部空間)には、グリースが配置されている。このグリースは、玉10,12、外輪8、内輪6の相互の摩擦を低減させる(図1参照)。 Between the outer ring 8 and the inner ring 6, grease is arranged in the space on the outboard side of the disc portion 45 (internal space of the hub bearing 1). This grease reduces the mutual friction between the balls 10, 12, the outer ring 8 and the inner ring 6 (see FIG. 1).
 グリースリップ46は、円板部45の径方向内端の弾性部分から径方向内側かつアウトボード側に向けて斜めに延びる、円錐台形状または円錐筒状の形状の薄板である。グリースリップ46の先端はスリーブ31Aの外周面に接触する。グリースリップ46は、ハブベアリング1の内部空間からインボード側へのグリースの流出を阻止する。 The grease lip 46 is a thin plate in the shape of a truncated cone or a cylindrical cone extending obliquely from the elastic portion at the radially inner end of the disk portion 45 toward the radially inner side and the outboard side. The tip of the grease lip 46 contacts the outer peripheral surface of the sleeve 31A. The grease lip 46 prevents grease from flowing out from the internal space of the hub bearing 1 to the inboard side.
 シールリップ47は、円板部45の径方向内端の弾性部分からインボード側に向けて延びる円環部49に形成された隆起である。円環部49も弾性環41から構成されている。第1のシール部材30と第2のシール部材40が組み合わせられない初期状態では、この隆起は仮想線で示す三角形の断面を有する。シールリップ47は、スリーブ31Aの外周面に接触し、グリースリップ46をバックアップする。すなわち、アウトボード側からグリースリップ46を通過したグリースのインボード側への流出を阻止する。 The seal lip 47 is a protrusion formed on the annular portion 49 extending from the elastic portion at the radially inner end of the disk portion 45 toward the inboard side. The annular portion 49 is also composed of the elastic ring 41 . In the initial state when the first sealing member 30 and the second sealing member 40 are not assembled, this ridge has a triangular cross-section shown in phantom lines. The seal lip 47 contacts the outer peripheral surface of the sleeve 31A and backs up the grease lip 46 . In other words, the grease that has passed through the grease lip 46 from the outboard side is prevented from flowing out to the inboard side.
 円環部49の外周にはガータースプリング50が巻かれている。ガータースプリング50は、シールリップ47に径方向内側への圧縮力を与え、スリーブ31Aに対するシールリップ47の緊縛力を高める。 A garter spring 50 is wound around the outer circumference of the annular portion 49 . The garter spring 50 exerts a radially inward compressive force on the seal lip 47 to increase the tightening force of the seal lip 47 against the sleeve 31A.
 サイドリップ48は、円板部45の弾性部分からフランジ31Bに向けて延びる薄板である。サイドリップ48は弾性環41から構成されている。サイドリップ48は、円板部45に隣接する厚い基部51と、基部51から径方向外側かつフランジ31Bに向けて斜めに延びて円錐台形状または円錐筒状の形状を有する薄い先端部52を有する。外輪8および第2のシール部材40の低速回転時には、サイドリップ48の先端部52は、フランジ31Bに摺動可能に接触する。 The side lip 48 is a thin plate extending from the elastic portion of the disc portion 45 toward the flange 31B. The side lip 48 is composed of the elastic ring 41 . The side lip 48 has a thick base portion 51 adjacent to the disk portion 45, and a thin tip portion 52 extending radially outward from the base portion 51 and obliquely toward the flange 31B and having a truncated cone shape or a conical tubular shape. . During low speed rotation of the outer ring 8 and the second seal member 40, the tip portion 52 of the side lip 48 slidably contacts the flange 31B.
 管状部44は、第1のシール部材30のフランジ31Bの外端縁のさらに外側に配置されている。管状部44と第1のシール部材30のフランジ31Bの間には、環状の間隙54が設けられている。ハブベアリング1の外部から間隙54を通じて、第1のシール部材30のフランジ31Bと第2のシール部材40の円板部45の間の空間55に異物が侵入しうる。逆に、異物が空間55から間隙54を通じて外部に排出されうる。 The tubular portion 44 is arranged further outside the outer edge of the flange 31B of the first seal member 30 . An annular gap 54 is provided between the tubular portion 44 and the flange 31B of the first seal member 30 . Foreign matter may enter the space 55 between the flange 31B of the first seal member 30 and the disk portion 45 of the second seal member 40 through the gap 54 from the outside of the hub bearing 1 . Conversely, foreign matter can be discharged from the space 55 to the outside through the gap 54 .
 外輪8および第2のシール部材40の低速回転時(回転速度が閾値より小さい場合)には、サイドリップ48は、第1のシール部材30のフランジ31Bに接触し、空間55の内部に侵入した異物がシールリップ47に向けてさらに侵入しないように阻止する役割を有する。低速回転時とは、外輪8および第2のシール部材40の回転が停止している時を含む。上記閾値は、例えば、回転速度(または回転数)であり、閾値は、一定の値であってもよく、変化する値であってもよい。例えば、閾値は、密封装置20の使用時間等に伴って変化(継時変化)することもあり、また、密封装置20の雰囲気温度等の使用態様に応じて変化することもある。フランジ31Bから第2のシール部材40に与えられるトルクを低減するため、サイドリップ48にはグリースがコートされてもよい。このグリースは、典型的には玉10,12、外輪8、内輪6を潤滑するグリースとは別種である。 When the outer ring 8 and the second seal member 40 rotate at a low speed (when the rotation speed is smaller than the threshold value), the side lip 48 contacts the flange 31B of the first seal member 30 and enters the space 55. It has the role of preventing foreign matter from further entering toward the seal lip 47 . The time of low speed rotation includes the time when the rotation of the outer ring 8 and the second seal member 40 is stopped. The threshold is, for example, the rotational speed (or number of revolutions), and the threshold may be a constant value or a variable value. For example, the threshold value may change (change over time) with the usage time of the sealing device 20, or may change according to the manner of use such as the ambient temperature of the sealing device 20. The side lip 48 may be coated with grease to reduce the torque imparted to the second seal member 40 from the flange 31B. This grease is different from the grease that typically lubricates the balls 10, 12, outer ring 8 and inner ring 6.
 一方、外輪8および第2のシール部材40の高速回転時(回転速度が閾値より大きい場合)には、図3に示すように、サイドリップ48、特に先端部52は、サイドリップ48自身にかかる遠心力によって、第1のシール部材30のフランジ31Bから離れるよう変形する。したがって、サイドリップ48の先端部52とフランジ31Bの間に、円環状の間隙56が設けられる。外輪回転型のハブベアリング1に使用される密封装置20においては、外輪8に固定される第2のシール部材40に遠心力がかかるからである。このように、サイドリップ48に大きい遠心力がかかると、先端部52がフランジ31Bから離れるように、サイドリップ48の寸法は設計されている。 On the other hand, when the outer ring 8 and the second seal member 40 rotate at high speed (when the rotational speed is greater than the threshold value), the side lip 48, particularly the tip portion 52, is applied to the side lip 48 itself, as shown in FIG. The centrifugal force deforms the first seal member 30 away from the flange 31B. Therefore, an annular gap 56 is provided between the tip portion 52 of the side lip 48 and the flange 31B. This is because centrifugal force is applied to the second seal member 40 fixed to the outer ring 8 in the sealing device 20 used in the outer ring rotating type hub bearing 1 . Thus, the dimensions of the side lip 48 are designed so that the tip 52 is separated from the flange 31B when a large centrifugal force is applied to the side lip 48 .
 外輪8および第2のシール部材40の高速回転時には、サイドリップ48がフランジ31Bから離れるが、第2のシール部材40自体が高速で回転しているので、空間55の内部には径方向外側に向かう気流又は遠心力が生じ、空間55の内部に侵入した異物が間隙54を通じて外部に排出される。また、サイドリップ48の径方向内部の空間57からも気流又は遠心力によって異物が間隙56を通じて、空間55に排出され、さらに間隙54を通じて外部に排出される。 When the outer ring 8 and the second seal member 40 rotate at high speed, the side lip 48 separates from the flange 31B. A directed air current or centrifugal force is generated, and foreign matter that has entered the space 55 is discharged to the outside through the gap 54 . Also, foreign matter is discharged from the space 57 radially inside the side lip 48 through the gap 56 to the space 55 by airflow or centrifugal force, and is further discharged to the outside through the gap 54 .
 以上のように、回転する外輪8に取り付けられた第2のシール部材40のサイドリップ48は、外輪8の回転速度が閾値より小さい場合には、フランジ31Bに摺動可能に接触し、密封装置20の封止性能を確保する。すなわち、サイドリップ48は、空間55に侵入した異物がシールリップ47に向けてさらに侵入しないように阻止する。 As described above, the side lip 48 of the second seal member 40 attached to the rotating outer ring 8 slidably contacts the flange 31B when the rotational speed of the outer ring 8 is less than the threshold value, and the sealing device 20 sealing performance is ensured. That is, the side lip 48 prevents foreign matter that has entered the space 55 from further entering toward the seal lip 47 .
 一方、外輪8の回転速度が閾値より大きい場合には、第2のシール部材40のサイドリップ48は、サイドリップ48自身にかかる遠心力によって、フランジ31Bから離れるよう変形する。したがって、回転する外輪8にかかるトルクが小さく、サイドリップ48の摩耗、摩擦熱による温度の上昇が抑制される。 On the other hand, when the rotational speed of the outer ring 8 is higher than the threshold, the side lip 48 of the second seal member 40 deforms away from the flange 31B due to the centrifugal force acting on the side lip 48 itself. Therefore, the torque applied to the rotating outer ring 8 is small, and the wear of the side lip 48 and the increase in temperature due to frictional heat are suppressed.
 図4は、本発明の第1の実施形態に係る密封装置20の他の使用形態を例示すための図である。密封装置20は、例えば図4に示すようなインホイールモータユニットにも用いることができる。インホイールモータユニットは、ハブベアリングとモータとが一体になって構成する駆動装置であり、車両の車輪に取り付けられ、モータ出力をハブベアリングを介して車輪に供給して車輪に動力を与え、また、車輪の動力をモータジェネレータを介して電力に変換して電気を発生する。 FIG. 4 is a diagram illustrating another usage pattern of the sealing device 20 according to the first embodiment of the present invention. The sealing device 20 can also be used, for example, in an in-wheel motor unit as shown in FIG. An in-wheel motor unit is a driving device that is configured by integrating a hub bearing and a motor. , converts the power of the wheels into electric power through a motor generator to generate electricity.
 例えば図4に示すように、インホイールモータユニット100は、内輪回転型のハブベアリング3と、ハブベアリング3に取り付けられた外側部材としての外側ケーシング101、内側部材としての内側ケーシング102、およびモータジェネレータ103とを備えている。具体的には、外側ケーシング101は、筒状の部材であり、ハブベアリング3を収容する内側の空間を形成している。外側ケーシング101は、ハブベアリング3の内輪7が備えるハブフランジ18とハブフランジ18に取り付けられるブレーキディスク110との間に挟まれ、ハブボルト19によって内輪7に車輪を固定することにより、ハブフランジ18とブレーキディスク110との間に固定される。 For example, as shown in FIG. 4, the in-wheel motor unit 100 includes an inner ring rotating hub bearing 3, an outer casing 101 as an outer member attached to the hub bearing 3, an inner casing 102 as an inner member, and a motor generator. 103. Specifically, the outer casing 101 is a tubular member and forms an inner space for housing the hub bearing 3 . The outer casing 101 is sandwiched between a hub flange 18 provided on the inner ring 7 of the hub bearing 3 and a brake disc 110 attached to the hub flange 18 , and by fixing the wheel to the inner ring 7 with hub bolts 19 , the hub flange 18 and the brake disc 110 are attached. It is fixed between the brake disc 110 .
 内側ケーシング102は、ハブベアリング3の外輪9を収容する内側の空間を形成している筒状の部材である筒部102aと、筒部102aのインボード側の端部から径方向外側に広がる円板状の部分である円板部102bとを有している。筒部102aは、外輪9が内側の空間に嵌合されて固定されるような形状となっている。 The inner casing 102 includes a tubular portion 102a, which is a tubular member forming an inner space for accommodating the outer ring 9 of the hub bearing 3, and a circular portion extending radially outward from the inboard-side end of the tubular portion 102a. It has a disk portion 102b which is a plate-like portion. The cylindrical portion 102a has a shape in which the outer ring 9 is fitted and fixed in the inner space.
 外側ケーシング101および内側ケーシング102は、図4に示すように、外側ケーシング101の径方向内側の面と、内側ケーシング102の筒部102aの径方向外側の面とが互いに対向して、外側ケーシング101と筒部102aとの間に環状の空間が形成される形状となっている。また、外側ケーシング101および内側ケーシング102は、図4に示すように、外側ケーシング101のインボード側の端部(端部101a)が、中心軸線Ax方向において内側ケーシング102の円板部102bに対向する形状となっている。外側ケーシング101の端部101aと円板部102bとの間には環状の隙間が形成されている。 As shown in FIG. 4, the outer casing 101 and the inner casing 102 are arranged such that the radially inner surface of the outer casing 101 and the radially outer surface of the cylindrical portion 102a of the inner casing 102 face each other. and the cylindrical portion 102a. As shown in FIG. 4, the outer casing 101 and the inner casing 102 have an inboard-side end (end 101a) of the outer casing 101 facing the disk portion 102b of the inner casing 102 in the central axis Ax direction. It has a shape that An annular gap is formed between the end portion 101a of the outer casing 101 and the disk portion 102b.
 モータジェネレータ103は、中心軸線Axに沿って延びる筒状の部材であり、外側ケーシング101と内側ケーシング102の筒部102aとの間の環状の空間に設けられている。モータジェネレータ103は、具体的には、ロータ104と、ステータ105とを備えており、ロータ104は外側ケーシング101に固定されており、ステータ105は、内側ケーシング102の筒部102aに固定されている。 The motor generator 103 is a tubular member that extends along the central axis Ax, and is provided in an annular space between the outer casing 101 and the tubular portion 102a of the inner casing 102 . Specifically, the motor generator 103 includes a rotor 104 and a stator 105. The rotor 104 is fixed to the outer casing 101, and the stator 105 is fixed to the cylindrical portion 102a of the inner casing 102. .
 インホイールモータユニット100において、密封装置20は、外側ケーシング101の端部101aと内側ケーシング102の円板部102bとの間の環状の隙間から、インホイールモータユニット100の内部に、異物が侵入することを防ぐために設けられている。例えば図4に示すように、密封装置20は、外側ケーシング101の端部101aと内側ケーシング102の円板部102bとの間に取り付けられている。具体的には、第1のシール部材30のスリーブ31Aが、内側ケーシング102の円板部102bの取付面102cに締まり嵌め方式で嵌着されて、第1のシール部材30は内側ケーシング102の円板部102bに固定されている。また、具体的には、第2のシール部材40の管状部44が、外側ケーシング101の端部101aの取付面101bに締まり嵌め方式で嵌着されて、第2のシール部材40は外側ケーシング101に固定されている。なお、内側ケーシング102の円板部102bの取付面102cは、中心軸線Axに沿って延びる円筒面状の面であり、外側ケーシング101の端部101aの取付面101bは、中心軸線Axに沿って延びる円筒面状の面である。また、取付面101bと取付面102cとは、径方向において互いに対向している。 In the in-wheel motor unit 100, the sealing device 20 prevents foreign matter from entering the in-wheel motor unit 100 through the annular gap between the end portion 101a of the outer casing 101 and the disk portion 102b of the inner casing 102. provided to prevent this. For example, as shown in FIG. 4 , the sealing device 20 is attached between the end portion 101 a of the outer casing 101 and the disk portion 102 b of the inner casing 102 . Specifically, the sleeve 31A of the first seal member 30 is fitted to the mounting surface 102c of the disc portion 102b of the inner casing 102 by an interference fit, so that the first seal member 30 is mounted on the inner casing 102. It is fixed to the plate portion 102b. Further, more specifically, the tubular portion 44 of the second seal member 40 is fitted to the mounting surface 101b of the end portion 101a of the outer casing 101 by an interference fit, so that the second seal member 40 is attached to the outer casing 101. is fixed to The mounting surface 102c of the disk portion 102b of the inner casing 102 is a cylindrical surface extending along the central axis Ax, and the mounting surface 101b of the end portion 101a of the outer casing 101 extends along the central axis Ax. It is an elongated cylindrical surface. Moreover, the mounting surface 101b and the mounting surface 102c face each other in the radial direction.
 密封装置20は、インホイールモータユニット100においても、上述のハブベアリング1に取り付けられた場合と同様に作用する(図3参照)。具体的には、回転する外側ケーシング101に取り付けられた第2のシール部材40のサイドリップ48は、外側ケーシング101および第2のシール部材40の回転速度が閾値より小さい低速回転時には、フランジ31Bに摺動可能に接触し、密封装置20の封止性能を確保する。すなわち、サイドリップ48は、空間55に侵入した異物がシールリップ47に向けてさらに侵入しないように異物の侵入を阻止する。一方、外側ケーシング101および第2のシール部材40の回転速度が閾値より大きい高速回転時には、第2のシール部材40のサイドリップ48は、サイドリップ48自身にかかる遠心力によって、フランジ31Bから離れる方向に変形して、間隙56が形成される。したがって、回転する外側ケーシング101にかかるトルクは小さく、また、サイドリップ48の摩耗、摩擦熱による温度の上昇が抑制される。 The sealing device 20 works in the in-wheel motor unit 100 in the same way as when it is attached to the hub bearing 1 described above (see FIG. 3). Specifically, the side lip 48 of the second seal member 40 attached to the rotating outer casing 101 is attached to the flange 31B when the rotation speed of the outer casing 101 and the second seal member 40 is lower than the threshold. The slidable contact ensures the sealing performance of the sealing device 20 . In other words, the side lip 48 prevents foreign matter from entering the space 55 from further entering toward the seal lip 47 . On the other hand, when the rotation speed of the outer casing 101 and the second seal member 40 is higher than the threshold, the side lip 48 of the second seal member 40 moves away from the flange 31B due to the centrifugal force acting on the side lip 48 itself. and a gap 56 is formed. Therefore, the torque applied to the rotating outer casing 101 is small, and the wear of the side lip 48 and temperature rise due to frictional heat are suppressed.
 また、外側ケーシング101および第2のシール部材40の高速回転時には、サイドリップ48がフランジ31Bから離れるが、第2のシール部材40自体が高速で回転しているので、空間55の内部には径方向外側に向かう気流又は遠心力が生じ、空間55の内部に侵入した異物が間隙54を通じて外部に排出される。また、サイドリップ48の径方向内部の空間57からも気流又は遠心力によって異物が間隙56を通じて、空間55に排出され、さらに間隙54を通じて外部に排出される。 When the outer casing 101 and the second seal member 40 rotate at high speed, the side lip 48 separates from the flange 31B. An outward air current or centrifugal force is generated, and foreign matter that has entered the space 55 is discharged to the outside through the gap 54 . Also, foreign matter is discharged from the space 57 radially inside the side lip 48 through the gap 56 to the space 55 by airflow or centrifugal force, and is further discharged to the outside through the gap 54 .
 インホイールモータユニットには、高速回転駆動させられるものがあり、このようなインホイールモータユニットにおいては、密封装置に基づくトルクの低減が求められる。本発明の第1の実施形態に係る密封装置20によれば、上述のように、外側ケーシング101の回転速度が閾値より大きい高速回転時に、回転する外側ケーシング101にかかるトルクを小さくすることができる。また、外側ケーシング101の回転速度が閾値より大きい高速回転時に、サイドリップ48の摩耗、摩擦熱による温度の上昇を抑制することができ、密封装置20の性能低下や寿命の低下を抑制することができる。一方、この高速回転時に、径方向外側に向かう気流又は遠心力が生じるため、異物の侵入を抑制することができる。このように、本発明の第1の実施形態に係る密封装置20は、インホイールモータにも好適に用いることができる。 Some in-wheel motor units are driven to rotate at high speed, and such in-wheel motor units are required to reduce torque based on sealing devices. According to the sealing device 20 according to the first embodiment of the present invention, as described above, the torque applied to the rotating outer casing 101 can be reduced when the outer casing 101 rotates at a high speed higher than the threshold. . In addition, when the outer casing 101 rotates at a high speed higher than the threshold value, it is possible to suppress wear of the side lip 48 and increase in temperature due to frictional heat, thereby suppressing performance degradation and shortening of the life of the sealing device 20. can. On the other hand, during this high-speed rotation, an air current directed radially outward or centrifugal force is generated, so that the intrusion of foreign matter can be suppressed. Thus, the sealing device 20 according to the first embodiment of the present invention can be suitably used also for in-wheel motors.
 次いで、本発明の第2の実施形態に係る密封装置21について説明する。本発明の第2の実施形態に係る密封装置21は、上述の本発明の第1の実施形態に係る密封装置20に対して、第2のシール部材の構成が異なる。また、本発明の第2の実施形態に係る密封装置21は、内輪回転型の適用対象に用いられ、適用対象において上述の密封装置20と異なる。以下、密封装置21の構成について、密封装置20と同じ構成又は同様の機能を有する構成については同じ符号を付してその説明を省略し、異なる構成について説明する。 Next, a sealing device 21 according to a second embodiment of the invention will be described. A sealing device 21 according to the second embodiment of the present invention differs from the above-described sealing device 20 according to the first embodiment of the present invention in the configuration of the second sealing member. Further, the sealing device 21 according to the second embodiment of the present invention is used for an inner ring rotating type, and is different from the above-described sealing device 20 in terms of application. In the following, with regard to the configuration of the sealing device 21, the same reference numerals are given to the same configurations or configurations having the same functions as those of the sealing device 20, and the description thereof will be omitted, and the different configurations will be described.
 図5に示すように、環状の密封装置21は、上述の密封装置20の第1のシール部材30と、密封装置20の第2のシール部材40とは異なる第2のシール部材60とを備えている。第2のシール部材60は、上述の密封装置20の第2のシール部材40の剛性環42を有しており、また、上述の密封装置20の第2のシール部材40の弾性環41とは異なる弾性環61を有している。なお、図5においては、密封装置21の軸線xに対する一方の部分のみが示されている。また、図5において、密封装置21は、後述する使用状態における状態(配置)で示されている。 As shown in FIG. 5, the annular sealing device 21 includes the first sealing member 30 of the sealing device 20 described above and a second sealing member 60 different from the second sealing member 40 of the sealing device 20. ing. The second seal member 60 has the rigid ring 42 of the second seal member 40 of the sealing device 20 described above. It has a different elastic ring 61 . 5, only one portion of the sealing device 21 with respect to the axis x is shown. In addition, in FIG. 5, the sealing device 21 is shown in a state (arrangement) in use, which will be described later.
 弾性環61は、密封装置20の第2のシール部材40の弾性環41と同様に、弾性材料、例えばエラストマーで形成されている。弾性環61は、弾性環41と同様に剛性環42に取り付けられており、具体的には、弾性環61は、剛性環42の一部に密着しており、また、剛性環42の一部は、弾性環61に埋設されている。 The elastic ring 61 is made of an elastic material, such as an elastomer, like the elastic ring 41 of the second seal member 40 of the sealing device 20 . The elastic ring 61 is attached to the rigid ring 42 in the same manner as the elastic ring 41 . are embedded in the elastic ring 61 .
 第2のシール部材60の弾性環61は、図5に示すように、第2のシール部材40の弾性環41と同様に、管状部44の部分、円板部45の部分およびサイドリップ62を有しているが、第2のシール部材40の弾性環41とは異なり、グリースリップ(ラジアルリップ)46およびシールリップ(ラジアルリップ)47を有していない。また、第2のシール部材60は、第2のシール部材40とは異なり、円環部49およびガータースプリング50を有していない。 The elastic ring 61 of the second sealing member 60, as shown in FIG. However, unlike the elastic ring 41 of the second seal member 40 , it does not have a grease lip (radial lip) 46 and a seal lip (radial lip) 47 . Also, unlike the second seal member 40 , the second seal member 60 does not have the annular portion 49 and the garter spring 50 .
 サイドリップ62は、第2のシール部材40のサイドリップ48と同様の形状を有しており、円板部45の弾性部分からフランジ31Bに向けて延びる薄板状の弾性環61の部分である。サイドリップ62は、円板部45に隣接する環状の厚い基部62aと、基部62aから径方向外側かつフランジ31Bに向けて斜めに延びて円錐台形状又は円錐筒状の形状を有する環状の薄い先端部62bとを有している。 The side lip 62 has the same shape as the side lip 48 of the second seal member 40, and is part of the thin plate-like elastic ring 61 extending from the elastic portion of the disk portion 45 toward the flange 31B. The side lip 62 has an annular thick base portion 62a adjacent to the disk portion 45, and an annular thin distal end extending radially outward from the base portion 62a and obliquely toward the flange 31B and having a truncated cone shape or a conical cylindrical shape. and a portion 62b.
 図5に示すように、第1のシール部材30は、第2のシール部材60を径方向外側から覆うように配置される。このため、使用状態において、第2のシール部材60は、第1のシール部材30よりも径方向内側に固定される。また、第1のシール部材30のフランジ31Bは、アウトボード側に面し、第2のシール部材60の円板部45は、インボード側に面する。 As shown in FIG. 5, the first sealing member 30 is arranged so as to cover the second sealing member 60 from the outside in the radial direction. Therefore, in use, the second seal member 60 is fixed radially inward of the first seal member 30 . The flange 31B of the first seal member 30 faces the outboard side, and the disk portion 45 of the second seal member 60 faces the inboard side.
 後述する密封装置21の使用状態において、密封装置21の適用対象およびサイドリップ62の低速回転時(回転速度が閾値より小さい場合)には、サイドリップ62の先端部62bが、フランジ31Bに摺動可能に接触するように、サイドリップ62は設計されている。一方、密封装置21の適用対象およびサイドリップ62の高速回転時(回転速度が閾値より大きい場合)には、サイドリップ62が変形して、サイドリップ62の先端部62bがフランジ31Bから離れる方向に移動するように、サイドリップ62は設計されている。ただし、密封装置21の適用対象およびサイドリップ62の高速回転時においても、サイドリップ62の先端部62bとフランジ31Bとの接触は維持されるように、サイドリップ62は設計されている。 In the usage state of the sealing device 21 described later, when the sealing device 21 is applied and the side lip 62 rotates at a low speed (when the rotation speed is smaller than the threshold value), the tip portion 62b of the side lip 62 slides on the flange 31B. Side lips 62 are designed to allow contact. On the other hand, when the sealing device 21 is applied and the side lip 62 rotates at high speed (when the rotation speed is greater than the threshold value), the side lip 62 deforms and the tip 62b of the side lip 62 moves away from the flange 31B. The side lip 62 is designed to move. However, the side lip 62 is designed so that the contact between the tip portion 62b of the side lip 62 and the flange 31B is maintained even when the sealing device 21 is applied and the side lip 62 rotates at high speed.
 密封装置21においても、図5に示すように、第2のシール部材60の管状部44と、第1のシール部材30のフランジ31Bの外端縁31Btとの間には、環状の間隙54が設けられている。つまり、使用状態において、管状部44のアウトボード側の端部44aは、フランジ31Bの外端縁31Btに径方向において間隔を空けて対向しており、管状部44の端部44aとフランジ31Bの外端縁31Btとの間には、間隙54が形成されている。間隙54は、ラビリンスシールを形成する。 Also in the sealing device 21, an annular gap 54 is formed between the tubular portion 44 of the second sealing member 60 and the outer edge 31Bt of the flange 31B of the first sealing member 30, as shown in FIG. is provided. That is, in use, the outboard-side end portion 44a of the tubular portion 44 faces the outer edge 31Bt of the flange 31B with a space therebetween in the radial direction. A gap 54 is formed between it and the outer edge 31Bt. Gap 54 forms a labyrinth seal.
 また、図5に示すように、第2のシール部材60の円板部45と、第1のシール部材30のスリーブ31Aとの間には、環状の間隙63が設けられている。つまり、使用状態において、第2のシール部材60の円板部45の外側の縁である外端縁45aは、第1のシール部材30のスリーブ31Aのインボード側の部分(部分31Ap)に径方向において間隔を空けて対向しており、円板部45の外端縁45aとスリーブ31Aの部分31Apとの間には、間隙63が形成されている。間隙63は、ラビリンスシールを形成する。 Further, as shown in FIG. 5, an annular gap 63 is provided between the disc portion 45 of the second seal member 60 and the sleeve 31A of the first seal member 30. As shown in FIG. In other words, when in use, the outer edge 45a of the disk portion 45 of the second seal member 60 is aligned with the inboard side portion (portion 31Ap) of the sleeve 31A of the first seal member 30. A gap 63 is formed between the outer edge 45a of the disk portion 45 and the portion 31Ap of the sleeve 31A. Gap 63 forms a labyrinth seal.
 次いで、上述の構成を有する密封装置21の作用について説明する。密封装置21は、適用対象に取り付けられて使用状態になる。密封装置21の適用対象は、例えばハブベアリングであり、密封装置21の適用対象のハブベアリングは、内輪回転型のハブベアリングである。図6は、密封装置21が取り付けられた密封装置21の適用対象としてのハブベアリング4の断面図である。 Next, the action of the sealing device 21 having the above configuration will be described. The sealing device 21 is attached to an application and is ready for use. The application target of the sealing device 21 is, for example, a hub bearing, and the hub bearing to which the sealing device 21 is applied is an inner ring rotation type hub bearing. FIG. 6 is a cross-sectional view of the hub bearing 4 to which the sealing device 21 is attached and to which the sealing device 21 is applied.
 図6に示すように、ハブベアリング4は、内輪120と外輪130とを備え、これらの内輪120と外輪130との間には、1列に配置された複数の玉10と、1列に配置された複数の玉12と、これらの玉を定位置に保持する複数の保持器14,15とが設けられている。内輪120と外輪130とは、転動体である玉10,12が設けられることによって、中心軸線Axで示す同軸上を互いに相対回転自在とされている。具体的には、車両等に取り付けられたハブベアリング4の使用状態において、外輪130は例えば車両の懸架装置に固定され、内輪120は外輪130に対して相対回動可能になる。内輪120は、具体的には、内側輪121とハブ輪122とを有しており、ハブ輪122は、中心軸線Axに沿って延びる筒状の軸部123と、ハブフランジ124とを有している。ハブフランジ124は、軸部123のアウトボード側の一端から径方向外側に向かって円板状に広がる部分であり、図示しない車輪が複数本のハブボルト19によって取り付けられる部分である。内側輪121は、内輪120と外輪130との間の空間内に玉10,12を保持するために、内輪120の軸部123のインボード側の端部に嵌合されている。 As shown in FIG. 6, the hub bearing 4 has an inner ring 120 and an outer ring 130. Between the inner ring 120 and the outer ring 130 are a plurality of balls 10 arranged in a row and a plurality of balls 10 arranged in a row. A plurality of balls 12 are provided and a plurality of retainers 14, 15 for holding the balls in place. The inner ring 120 and the outer ring 130 are provided with the balls 10 and 12, which are rolling elements, so that the inner ring 120 and the outer ring 130 are rotatable relative to each other on the same axis indicated by the center axis Ax. Specifically, when the hub bearing 4 attached to a vehicle or the like is used, the outer ring 130 is fixed to, for example, a suspension system of the vehicle, and the inner ring 120 is rotatable relative to the outer ring 130 . Specifically, the inner ring 120 has an inner ring 121 and a hub ring 122. The hub ring 122 has a cylindrical shaft portion 123 extending along the center axis Ax and a hub flange 124. ing. The hub flange 124 is a portion extending radially outward from one end of the shaft portion 123 on the outboard side in a disc shape, and is a portion to which wheels (not shown) are attached by a plurality of hub bolts 19 . The inner ring 121 is fitted to the inboard end of the shaft portion 123 of the inner ring 120 to hold the balls 10 and 12 in the space between the inner ring 120 and the outer ring 130 .
 外輪130は、中心軸線Ax方向に延びる貫通孔131を有しており、この貫通孔131には、内輪120のハブ輪122の軸部123と内側輪121とが挿入されており、内側輪121および軸部123と貫通孔131との間に中心軸線Axに沿って延びる環状の空間が形成されている。この空間内には、上述のように玉10,12が収容されて保持器14,15によって保持されており、また、潤滑剤が塗布又は注入されている。内側輪121および軸部123と貫通孔131との間の空間がインボード側において開放された開口を形成するハブベアリング4のインボード側開口部126には、密封装置21が取り付けられ、内側輪121および軸部123と貫通孔131との間の空間がアウトボード側において開放された開口を形成するハブベアリング4のアウトボード側開口部127には、他の密封装置140が取り付けられている。密封装置21,140によって、ハブベアリング4の内部空間の密封が図られており、内部空間の潤滑剤が外部に漏れ出ることの防止が図られており、外部から異物が内部空間に侵入することの防止が図られている。密封装置140は、従来公知の密封装置であり、詳細な説明は省略する。なお、密封装置140として、密封装置21を適用することもできる。密封装置21が適用されるハブベアリングの構成は、上述のハブベアリング4の構成に限られない。 Outer ring 130 has a through hole 131 extending in the direction of central axis Ax. An annular space extending along the central axis Ax is formed between the shaft portion 123 and the through hole 131 . In this space, the balls 10, 12 are accommodated and held by the cages 14, 15 as described above, and a lubricant is applied or injected. A sealing device 21 is attached to an inboard side opening 126 of the hub bearing 4 in which the space between the inner ring 121 and the shaft portion 123 and the through hole 131 forms an opening opened on the inboard side. Another sealing device 140 is attached to an outboard-side opening 127 of the hub bearing 4 in which the space between 121 and the shaft portion 123 and the through hole 131 forms an opening opened on the outboard side. The internal space of the hub bearing 4 is sealed by the sealing devices 21 and 140 to prevent the lubricant in the internal space from leaking to the outside and prevent foreign matter from entering the internal space from the outside. are being prevented. The sealing device 140 is a conventionally known sealing device, and detailed description thereof will be omitted. Note that the sealing device 21 can also be applied as the sealing device 140 . The configuration of the hub bearing to which the sealing device 21 is applied is not limited to the configuration of the hub bearing 4 described above.
 具体的には、外輪130のインボード側の円筒状の端部130Aに、密封装置21の第1のシール部材30のスリーブ31Aが取り付けられ、また、内輪120の内側輪121のインボード側の円筒状の端部121Aに、密封装置21の第2のシール部材60の管状部44が取り付けられ、密封装置21はハブベアリング4に取り付けられる(図5参照)。第1のシール部材30のスリーブ31Aは、具体的には、外輪130の端部130Aに締り嵌め方式で嵌め入れられ、第2のシール部材60の管状部44は、具体的には、内側輪121の端部121Aに締り嵌め方式で嵌め入れられる。ハブベアリング4に取り付けられた密封装置21の軸線xは、ハブベアリング4の中心軸線Axに一致又は略一致する。 Specifically, the sleeve 31A of the first sealing member 30 of the sealing device 21 is attached to the cylindrical end portion 130A on the inboard side of the outer ring 130, and the inboard side of the inner ring 121 of the inner ring 120 is attached. The tubular portion 44 of the second sealing member 60 of the sealing device 21 is attached to the cylindrical end portion 121A, and the sealing device 21 is attached to the hub bearing 4 (see FIG. 5). Specifically, the sleeve 31A of the first sealing member 30 is fitted into the end portion 130A of the outer ring 130 in an interference fit, and the tubular portion 44 of the second sealing member 60 is specifically fitted to the inner ring. The end portion 121A of 121 is fitted by an interference fit method. The axis x of the sealing device 21 attached to the hub bearing 4 coincides or substantially coincides with the central axis Ax of the hub bearing 4 .
 上述のように、密封装置21はハブベアリング4に固定される。第1のシール部材30は、静止した外輪130に固定され、回転しない固定シール部材である。一方、第2のシール部材60は、回転する内輪120に固定され、回転する回転シール部材である。ハブベアリング4において密封装置21は、内輪120の回転速度に応じて異なった作用をする。 The sealing device 21 is fixed to the hub bearing 4 as described above. The first seal member 30 is a stationary seal member that is fixed to the stationary outer ring 130 and does not rotate. On the other hand, the second seal member 60 is a rotary seal member that is fixed to the rotating inner ring 120 and rotates. The sealing device 21 in the hub bearing 4 behaves differently depending on the rotational speed of the inner ring 120 .
 具体的には、内輪120および第2のシール部材60の低速回転時(回転速度が閾値より小さい場合)には、図5に示すように、サイドリップ62は、第1のシール部材30のフランジ31Bに接触し、空間55の内部に侵入した異物がハブベアリング4の内部空間に向けてさらに侵入しないように異物の侵入を阻止する役割を有する。低速回転時とは、内輪120および第2のシール部材60の回転が停止している時を含む。フランジ31Bから第2のシール部材60に与えられるトルクを低減するため、サイドリップ62にはグリースがコートされてもよい。このグリースは、典型的には玉10,12、内輪120、外輪130を潤滑するグリースとは別種である。 Specifically, when the inner ring 120 and the second seal member 60 rotate at a low speed (when the rotation speed is smaller than the threshold value), the side lip 62 is located on the flange of the first seal member 30 as shown in FIG. 31B and has a role of preventing foreign matter from entering the space 55 from further entering the inner space of the hub bearing 4. As shown in FIG. The time of low speed rotation includes the time when the rotation of the inner ring 120 and the second seal member 60 is stopped. The side lip 62 may be coated with grease to reduce torque applied to the second seal member 60 from the flange 31B. This grease is different from the grease that typically lubricates the balls 10, 12, inner ring 120, and outer ring 130.
 一方、内輪120および第2のシール部材60の高速回転時(回転速度が閾値より大きい場合)には、図5に点線で示すように、サイドリップ62、特に先端部62bは、サイドリップ62自身にかかる遠心力によって、第1のシール部材30のフランジ31Bから離れるよう変形する。ただし、サイドリップ62は、この高速回転時に加わる遠心力によって、フランジ31Bから完全に離れることがないように設計されている。このため、密封装置20とは異なり、内輪120および第2のシール部材60の高速回転時に、サイドリップ62の先端部62bとフランジ31Bの間に、円環状の間隙が設けられることはないが、サイドリップ62に加わる遠心力により、先端部62bとフランジ31Bとの間の締め代またはサイドリップ62の反力は低減する。これにより、内輪120の高速回転時に、サイドリップ62とフランジ31Bとの間の摺動抵抗を低減させることができ、回転する内輪120にかかるトルクを小さくすることができる。また、サイドリップ62の摩耗、摩擦熱による温度の上昇を抑制することができる。 On the other hand, when the inner ring 120 and the second seal member 60 rotate at a high speed (when the rotation speed is greater than the threshold value), the side lip 62, particularly the tip portion 62b, moves toward the side lip 62 itself, as indicated by the dotted line in FIG. is deformed away from the flange 31B of the first seal member 30 by the centrifugal force applied to the first seal member 30. As shown in FIG. However, the side lip 62 is designed so that it will not completely separate from the flange 31B due to the centrifugal force applied during high-speed rotation. Therefore, unlike the sealing device 20, an annular gap is not provided between the tip portion 62b of the side lip 62 and the flange 31B when the inner ring 120 and the second seal member 60 rotate at high speed. Due to the centrifugal force applied to the side lip 62, the interference between the tip 62b and the flange 31B or the reaction force of the side lip 62 is reduced. Thereby, when the inner ring 120 rotates at high speed, the sliding resistance between the side lip 62 and the flange 31B can be reduced, and the torque applied to the rotating inner ring 120 can be reduced. Also, it is possible to suppress the wear of the side lip 62 and the increase in temperature due to frictional heat.
 また、図5に示すように、第2のシール部材60の管状部44の端部44aと、第1のシール部材30のフランジ31Bの外端縁31Btとの間には、環状の間隙54が設けられており、間隙54はラビリンスシールとして機能する。このため、ハブベアリング4の内部空間に異物が侵入することが抑制されている。 5, an annular gap 54 is formed between the end portion 44a of the tubular portion 44 of the second seal member 60 and the outer edge 31Bt of the flange 31B of the first seal member 30. provided, the gap 54 functions as a labyrinth seal. Therefore, foreign matter is prevented from entering the internal space of the hub bearing 4 .
 一方、間隙54が形成するラビリンスシールによって、ハブベアリング4の内部空間から潤滑剤が流出することが防止されており、また、サイドリップ62によって、ハブベアリング4の外部に潤滑剤が流出することが防止されている。このように、密封装置21は、内輪120の回転速度に関わらず、間隙54及びサイドリップ62によって、ハブベアリング4の内部空間から潤滑剤が流出することを抑制することができる。 On the other hand, the labyrinth seal formed by the gap 54 prevents the lubricant from flowing out of the inner space of the hub bearing 4 , and the side lip 62 prevents the lubricant from flowing out of the hub bearing 4 . is prevented. In this manner, the sealing device 21 can prevent lubricant from flowing out of the internal space of the hub bearing 4 by the gap 54 and the side lip 62 regardless of the rotational speed of the inner ring 120 .
 また、図5に示すように、第2のシール部材60の円板部45の外端縁45aと、第1のシール部材30のスリーブ31Aの部分Apとの間には、環状の間隙63が設けられており、間隙63はラビリンスシールとして機能する。このため、ハブベアリング4の外部から密封装置21の内部の空間55に異物が侵入することが防止されている。このように、密封装置21は、間隙63によっても、ハブベアリング4の内部空間に異物が侵入することを抑制することができる。また、間隙63は、ハブベアリング4の外部に潤滑剤が流出することを抑制することができる。 As shown in FIG. 5, an annular gap 63 is formed between the outer edge 45a of the disk portion 45 of the second seal member 60 and the portion Ap of the sleeve 31A of the first seal member 30. provided, the gap 63 functions as a labyrinth seal. Therefore, foreign matter is prevented from entering the space 55 inside the sealing device 21 from the outside of the hub bearing 4 . In this manner, the sealing device 21 can prevent foreign matter from entering the internal space of the hub bearing 4 by the gap 63 as well. Also, the gap 63 can prevent the lubricant from flowing out of the hub bearing 4 .
 以上のように、回転する内輪120に取り付けられた第2のシール部材60のサイドリップ62は、内輪120の回転速度が閾値より小さい場合には、フランジ31Bに摺動可能に接触し、密封装置21の封止性能を確保する。すなわち、低速回転時において、サイドリップ62は、空間55に侵入した異物がハブベアリング4の内部空間に向けてさらに侵入しないように異物の侵入を阻止する。 As described above, the side lip 62 of the second seal member 60 attached to the rotating inner ring 120 slidably contacts the flange 31B when the rotational speed of the inner ring 120 is less than the threshold value, thereby closing the sealing device. 21 sealing performance is ensured. That is, during low-speed rotation, the side lip 62 prevents foreign matter from entering the space 55 and further entering the inner space of the hub bearing 4 .
 一方、内輪120の回転速度が閾値より大きい場合には、第2のシール部材60のサイドリップ62は、サイドリップ62自身にかかる遠心力によって、フランジ31Bとの接触が維持される範囲でフランジ31Bから離れるように変形する。したがって、高速回転時において、密封装置21は、封止性能を確保しつつ、回転する内輪120にかかるトルクを低減し、また、サイドリップ62の摩耗、摩擦熱による温度の上昇を抑制する。 On the other hand, when the rotational speed of the inner ring 120 is higher than the threshold, the side lip 62 of the second seal member 60 is rotated by the centrifugal force exerted on the side lip 62 itself to the extent that contact with the flange 31B is maintained. transform away from Therefore, during high-speed rotation, the sealing device 21 reduces the torque applied to the rotating inner ring 120 while ensuring sealing performance, and suppresses temperature rise due to wear of the side lip 62 and frictional heat.
 次いで、本発明の第3の実施形態に係る密封装置22について説明する。本発明の第3の実施形態に係る密封装置22は、上述の本発明の第1の実施形態に係る密封装置20に対して、第1のシール部材及び第2のシール部材の構成が異なる。また、本発明の第3の実施形態に係る密封装置22は、上述の本発明の第2の実施形態に係る密封装置21と同様に内輪回転型の適用対象に用いられ、適用対象において上述の密封装置20とは異なる。以下、密封装置22の構成について、密封装置20と同じ構成又は同様の機能を有する構成については同じ符号を付してその説明を省略し、異なる構成について説明する。 Next, a sealing device 22 according to a third embodiment of the invention will be described. A sealing device 22 according to the third embodiment of the present invention differs from the above-described sealing device 20 according to the first embodiment of the present invention in the configurations of the first sealing member and the second sealing member. Further, the sealing device 22 according to the third embodiment of the present invention is used for an inner ring rotation type application object like the sealing device 21 according to the second embodiment of the present invention. It differs from the sealing device 20 . Hereinafter, with respect to the configuration of the sealing device 22, the same reference numerals are given to the same configurations or configurations having the same functions as those of the sealing device 20, and the description thereof will be omitted, and the different configurations will be described.
 図7に示すように、環状の密封装置22は、上述の密封装置20の第1のシール部材30とは異なる第1のシール部材70と、密封装置20の第2のシール部材40とは異なる第2のシール部材65とを備えている。第1のシール部材70は、上述の密封装置20の第2のシール部材30の剛性環42と、弾性環71とを有している。また、第2のシール部材65は、上述の密封装置20の第1のシール部材30の剛性環31と、弾性環66とを有している。なお、図7においては、密封装置22の軸線xに対する一方の部分のみが示されている。また、図7において、密封装置22は、後述する使用状態における状態(配置)で示されている。 As shown in FIG. 7, the annular sealing device 22 has a first sealing member 70 different from the first sealing member 30 of the sealing device 20 described above and a second sealing member 40 of the sealing device 20. and a second sealing member 65 . The first seal member 70 has the rigid ring 42 of the second seal member 30 of the sealing device 20 described above and the elastic ring 71 . Also, the second seal member 65 has the rigid ring 31 of the first seal member 30 of the sealing device 20 described above and the elastic ring 66 . 7, only one portion of the sealing device 22 with respect to the axis x is shown. In addition, in FIG. 7, the sealing device 22 is shown in a state (arrangement) in use, which will be described later.
 図7に示すように、第1のシール部材70は、第2のシール部材65を径方向外側から覆うように配置される。このため、使用状態において、第2のシール部材65は、第1のシール部材70よりも径方向内側に固定される。また、第2のシール部材65のフランジ31Bは、インボード側に面し、第1のシール部材70の円板部45は、アウトボード側に面する。 As shown in FIG. 7, the first sealing member 70 is arranged so as to cover the second sealing member 65 from the outside in the radial direction. Therefore, in use, the second seal member 65 is fixed radially inward of the first seal member 70 . The flange 31B of the second seal member 65 faces the inboard side, and the disk portion 45 of the first seal member 70 faces the outboard side.
 第1のシール部材70の弾性環71は、弾性材料、例えばエラストマーで形成されている。弾性環71は、剛性環42に取り付けられており、具体的には、弾性環71は、剛性環42の一部に密着しており、また、剛性環42の一部は、弾性環71に埋設されている。弾性環71は、図7に示すように、密封装置20の第2のシール部材40の弾性環41の管状部44の部分と、第2のシール部材40の弾性環41の円板部45の径方向内側端の部分である内側端部72と、グリースリップ46と、シールリップ47とを有している。また、弾性環71は、内側端部72から延びる第2のシール部材40の円環部49を有している。また、第1のシール部材70は、第2のシール部材40と同様に、ガータースプリング50を有している。 The elastic ring 71 of the first seal member 70 is made of an elastic material such as an elastomer. The elastic ring 71 is attached to the rigid ring 42 . Specifically, the elastic ring 71 is in close contact with part of the rigid ring 42 , and part of the rigid ring 42 is attached to the elastic ring 71 . Buried. As shown in FIG. 7, the elastic ring 71 consists of the tubular portion 44 of the elastic ring 41 of the second seal member 40 of the sealing device 20 and the disk portion 45 of the elastic ring 41 of the second seal member 40. It has an inner end portion 72 which is part of the radially inner end, a grease lip 46 and a sealing lip 47 . The elastic ring 71 also has an annular portion 49 of the second seal member 40 extending from the inner end 72 . Also, the first seal member 70 has a garter spring 50 like the second seal member 40 .
 グリースリップ46とシールリップ47とは、密封装置20の第2のシール部材40のグリースリップ46とシールリップ47と同様に、円板部45の径方向内側に配置されており、スリーブ31Aに摺動可能に接触するように形成されている。具体的には、グリースリップ46は内側端部72から延びており、シールリップ47は、内側端部72から延びる円環部49に形成されている。 Like the grease lip 46 and the seal lip 47 of the second seal member 40 of the sealing device 20, the grease lip 46 and the seal lip 47 are arranged radially inside the disk portion 45 and slide on the sleeve 31A. configured for movably contact. Specifically, the grease lip 46 extends from the inner end 72 and the sealing lip 47 is formed on an annular portion 49 extending from the inner end 72 .
 図7に示すように、第1のシール部材70の円板部45において内側端部72よりも径方向外側の部分には、第1のシール部材70の弾性環71は形成されていない。このため、第1のシール部材70の円板部45において、剛性環42の内側端部72よりも径方向外側の部分は、露出されており、剛性環42は、内側端部72よりも径方向外側の円板部45の部分に、インボード側に面する円環状の面である接触面73を有している。 As shown in FIG. 7, the elastic ring 71 of the first seal member 70 is not formed in the portion of the disk portion 45 of the first seal member 70 radially outside the inner end portion 72 . Therefore, in the disk portion 45 of the first seal member 70 , a portion radially outside the inner end portion 72 of the rigid ring 42 is exposed, and the rigid ring 42 is radially larger than the inner end portion 72 . A contact surface 73 that is an annular surface facing the inboard side is provided on the portion of the disk portion 45 on the direction outer side.
 第2のシール部材65の弾性環66は、弾性材料、例えばエラストマーで形成されている。弾性環66は、図7に示すように、剛性環31に取り付けられており、具体的には、弾性環66は、剛性環31の一部に密着しており、また、剛性環31の一部は、弾性環66に埋設されている。 The elastic ring 66 of the second seal member 65 is made of an elastic material such as elastomer. The elastic ring 66 is attached to the rigid ring 31, as shown in FIG. The part is embedded in the elastic ring 66 .
 第2のシール部材65の弾性環66は、図7に示すように、剛性環31のフランジ31Bのアウトボード側の面に取り付けられている部分である基部67と、基部67から延びる部分であるサイドリップ68及びラビリンスリップ69とを有している。基部67は、軸線x周りに環状に延びており、径方向外側において、フランジ31Bの径方向外側の端部を覆うように形成されている。 The elastic ring 66 of the second seal member 65 is, as shown in FIG. It has a side lip 68 and a labyrinth lip 69 . The base portion 67 extends annularly around the axis x and is formed so as to cover the radially outer end portion of the flange 31B on the radially outer side.
 サイドリップ68は、図7に示すように、弾性環66の基部67のアウトボード側に面する面(面67a)から延びており、上述の密封装置20のサイドリップ48と同様の形状を有しており、第1のシール部材70の剛性環42の接触面73に向けて延びている薄板状の弾性環66の部分である。サイドリップ68は、例えば図7に示すように、基部67に隣接する環状の厚い基部68aと、基部68aから径方向外側かつ接触面73に向けて斜めに延びて円錐台形状又は円錐筒状の形状を有する環状の薄い先端部68bとを有している。 As shown in FIG. 7, the side lip 68 extends from the surface (surface 67a) facing the outboard side of the base portion 67 of the elastic ring 66, and has the same shape as the side lip 48 of the sealing device 20 described above. and is the portion of the thin plate-like elastic ring 66 that extends toward the contact surface 73 of the rigid ring 42 of the first seal member 70 . For example, as shown in FIG. 7, the side lip 68 has an annular thick base portion 68a adjacent to the base portion 67, and a truncated cone shape or a conical tubular shape extending radially outward from the base portion 68a and obliquely toward the contact surface 73. and an annular thin tip 68b having a shape.
 後述する密封装置22の使用状態において、密封装置22の適用対象および第2のシール部材65の低速回転時(回転速度が閾値より小さい場合)には、サイドリップ68の先端部68bが、剛性環42の接触面73に摺動可能に接触するように、サイドリップ68は設計されている。一方、密封装置22の適用対象および第2のシール部材65の高速回転時(回転速度が閾値より大きい場合)には、上述の密封装置20のサイドリップ48と同様に、サイドリップ68の先端部68bが、剛性環42の接触面73から離れるように変形するように、サイドリップ68は設計されている。なお、サイドリップ68は、密封装置22の適用対象および第2のシール部材65の高速回転時に、先端部68bが、剛性環42の接触面73から離れない範囲で接触面73から離れる方向に移動するように、設計されていてもよい。 When the sealing device 22 is used, which will be described later, when the sealing device 22 is applied and the second sealing member 65 rotates at a low speed (when the rotation speed is smaller than the threshold value), the tip 68b of the side lip 68 moves toward the rigid ring. The side lip 68 is designed to slidably contact the contact surface 73 of 42 . On the other hand, when the sealing device 22 is applied and the second sealing member 65 rotates at high speed (when the rotation speed is greater than the threshold value), the tip portion of the side lip 68 is Side lip 68 is designed such that 68b deforms away from contact surface 73 of rigid ring 42 . When the sealing device 22 is applied and the second seal member 65 rotates at high speed, the side lip 68 moves away from the contact surface 73 of the rigid ring 42 as long as the tip 68b does not move away from the contact surface 73 of the rigid ring 42. It may be designed to
 また、図7に示すように、第2のシール部材65のフランジ31Bの径方向外側端部を覆う基部67の部分である外側端部67bは、第1のシール部材70の管状部44のインボード側の端部における弾性環71の部分であるラビリンス受部71aに径方向において間隔を空けて対向するようになっている。このため、基部67の外側端部67bと管状部44のラビリンス受部71aとの間には、間隙74が形成される。 Further, as shown in FIG. 7, the outer end portion 67b, which is the portion of the base portion 67 that covers the radially outer end portion of the flange 31B of the second seal member 65, is located inside the tubular portion 44 of the first seal member 70. It faces a labyrinth receiving portion 71a, which is a portion of the elastic ring 71 at the end on the board side, with a gap in the radial direction. Therefore, a gap 74 is formed between the outer end portion 67 b of the base portion 67 and the labyrinth receiving portion 71 a of the tubular portion 44 .
 ラビリンスリップ69は、図7に示すように、基部67の外側端部67bからラビリンス受部71aに向かって延びており、ラビリンスリップ69の先端部69aは、ラビリンス受部71aに径方向において間隔を空けて対向するようになっている。このように、間隙74において、ラビリンスリップ69の先端部69aとラビリンス受部71aとの間には、間隙74をさらに狭める環状の間隙74aが形成されている。間隙74及び間隙74aは、ラビリンスシールを形成する。 As shown in FIG. 7, the labyrinth lip 69 extends from the outer end 67b of the base portion 67 toward the labyrinth receiving portion 71a. They are facing each other with a space between them. Thus, in the gap 74, an annular gap 74a is formed between the tip 69a of the labyrinth lip 69 and the labyrinth receiving portion 71a to further narrow the gap 74. As shown in FIG. Gap 74 and gap 74a form a labyrinth seal.
 次いで、上述の構成を有する密封装置22の作用について説明する。密封装置22は、適用対象に取り付けられて使用状態になる。密封装置22の適用対象は、例えばハブベアリングであり、密封装置22の適用対象のハブベアリングは、内輪回転型のハブベアリングである。密封装置22は、例えば上述の密封装置21が取り付けられるハブベアリング4に取り付けられる(図6参照)。なお、密封装置22が取り付けられたハブベアリング4の図示は省略されている。 Next, the action of the sealing device 22 having the above configuration will be described. The sealing device 22 is attached to an application and ready for use. The application target of the sealing device 22 is, for example, a hub bearing, and the hub bearing to which the sealing device 22 is applied is an inner ring rotation type hub bearing. The sealing device 22 is attached, for example, to the hub bearing 4 to which the sealing device 21 described above is attached (see FIG. 6). The illustration of the hub bearing 4 to which the sealing device 22 is attached is omitted.
 密封装置22は、密封装置21と同様に、ハブベアリング4のインボード側開口部126に取り付けられる。具体的には、外輪130のインボード側の端部130Aに、密封装置22の第1のシール部材70の管状部44が取り付けられ、また、内輪120の内側輪121のインボード側の端部121Aに、密封装置22の第2のシール部材65のスリーブ31Aが取り付けられ、密封装置22はハブベアリング4に取り付けられる(図6,7参照)。第1のシール部材70の管状部44は、具体的には、外輪130の端部130Aに締り嵌め方式で嵌め入れられ、第2のシール部材65のスリーブ31Aは、具体的には、内側輪121の端部121Aに締り嵌め方式で嵌め入れられる。ハブベアリング4に取り付けられた密封装置22の軸線xは、ハブベアリング4の中心軸線Axに一致又は略一致する。 The sealing device 22 is attached to the inboard side opening 126 of the hub bearing 4 in the same manner as the sealing device 21 . Specifically, the tubular portion 44 of the first sealing member 70 of the sealing device 22 is attached to the inboard side end portion 130A of the outer ring 130, and the inboard side end portion of the inner ring 121 of the inner ring 120 is attached. The sleeve 31A of the second sealing member 65 of the sealing device 22 is attached to 121A, and the sealing device 22 is attached to the hub bearing 4 (see FIGS. 6 and 7). The tubular portion 44 of the first sealing member 70 is specifically fitted to the end portion 130A of the outer ring 130 in an interference fit, and the sleeve 31A of the second sealing member 65 is specifically fitted to the inner ring. The end portion 121A of 121 is fitted by an interference fit method. The axis x of the sealing device 22 attached to the hub bearing 4 coincides or substantially coincides with the central axis Ax of the hub bearing 4 .
 上述のように、密封装置22はハブベアリング4に固定される。第1のシール部材70は、静止した外輪130に固定され、回転しない固定シール部材である。一方、第2のシール部材65は、回転する内輪120に固定され、回転する回転シール部材である。ハブベアリング4において密封装置22は、内輪120の回転速度に応じて異なった作用をする。 The sealing device 22 is fixed to the hub bearing 4 as described above. The first seal member 70 is fixed to the stationary outer ring 130 and is a stationary seal member that does not rotate. On the other hand, the second seal member 65 is a rotary seal member that is fixed to the rotating inner ring 120 and rotates. The sealing device 22 in the hub bearing 4 acts differently depending on the rotational speed of the inner ring 120 .
 具体的には、内輪120および第2のシール部材65の低速回転時(回転速度が閾値より小さい場合)には、図7に示すように、サイドリップ68は、第1のシール部材70の剛性環42の接触面73に接触し、空間55の内部に侵入した異物がハブベアリング4の内部空間に向けてさらに侵入しないように異物の侵入を阻止する役割を有する。低速回転時とは、内輪120および第2のシール部材65の回転が停止している時を含む。剛性環42の接触面73から第2のシール部材65に与えられるトルクを低減するため、サイドリップ68にはグリースがコートされてもよい。このグリースは、典型的には玉10,12、内輪120、外輪130を潤滑するグリースとは別種である。 Specifically, when the inner ring 120 and the second seal member 65 rotate at low speed (when the rotation speed is smaller than the threshold value), the side lip 68 reduces the rigidity of the first seal member 70 as shown in FIG. It contacts the contact surface 73 of the ring 42 and has a role of preventing foreign matter from entering the space 55 from further entering the inner space of the hub bearing 4 . The time of low speed rotation includes the time when the rotation of the inner ring 120 and the second seal member 65 is stopped. The side lip 68 may be coated with grease to reduce the torque imparted to the second seal member 65 from the contact surface 73 of the rigid ring 42 . This grease is different from the grease that typically lubricates the balls 10, 12, inner ring 120, and outer ring 130.
 一方、内輪120および第2のシール部材65の高速回転時(回転速度が閾値より大きい場合)には、図7に点線で示すように、サイドリップ68、特に先端部68aは、サイドリップ68自身にかかる遠心力によって、第1のシール部材70の剛性環42の接触面73から離れるよう変形する。このため、密封装置20と同様に、内輪120および第2のシール部材65の高速回転時に、サイドリップ68の先端部68aと剛性環42の接触面73の間に、円環状の間隙56が設けられる。これにより、内輪120の高速回転時に、サイドリップ68と剛性環42の接触面73との間の摺動抵抗をなくすことができ、回転する内輪120にかかるトルクを小さくすることができる。また、サイドリップ68の摩耗、摩擦熱による温度の上昇を抑制することができる。 On the other hand, when the inner ring 120 and the second seal member 65 rotate at a high speed (when the rotational speed is greater than the threshold value), the side lip 68, particularly the tip portion 68a, moves toward the side lip 68 itself, as indicated by the dotted line in FIG. is deformed away from the contact surface 73 of the rigid ring 42 of the first seal member 70 by the centrifugal force applied to the first seal member 70 . Therefore, similarly to the sealing device 20, when the inner ring 120 and the second seal member 65 rotate at high speed, an annular gap 56 is provided between the tip portion 68a of the side lip 68 and the contact surface 73 of the rigid ring 42. be done. As a result, sliding resistance between the side lip 68 and the contact surface 73 of the rigid ring 42 can be eliminated when the inner ring 120 rotates at high speed, and the torque applied to the rotating inner ring 120 can be reduced. Also, it is possible to suppress the wear of the side lip 68 and the increase in temperature due to frictional heat.
 また、図7に示すように、第2のシール部材65のラビリンスリップ69と、第1のシール部材70の管状部44のラビリンス受部71aとの間には、環状の間隙74,74aが設けられており、間隙74,74aはラビリンスシールとして機能する。このため、ハブベアリング4の外部から密封装置22の内部の空間55に異物が侵入することが防止されている。このように、密封装置22は、間隙74,74aによっても、ハブベアリング4の内部空間に異物が侵入することを抑制することができる。また、ハブベアリング4の外部に潤滑剤が流出することを抑制することができる。 7, annular gaps 74 and 74a are provided between the labyrinth lip 69 of the second seal member 65 and the labyrinth receiving portion 71a of the tubular portion 44 of the first seal member 70. The gaps 74, 74a function as labyrinth seals. Therefore, foreign matter is prevented from entering the space 55 inside the sealing device 22 from the outside of the hub bearing 4 . In this manner, the sealing device 22 can prevent foreign matter from entering the internal space of the hub bearing 4 by the gaps 74 and 74a. In addition, it is possible to prevent the lubricant from flowing out of the hub bearing 4 .
 また、グリースリップ46およびシールリップ47は、上述の密封装置20のグリースリップ46およびシールリップ47と同様に夫々作用する。つまり、グリースリップ46は、ハブベアリング4の内部空間からインボード側への潤滑剤の流出を阻止する。また、シールリップ47は、グリースリップ46をバックアップし、アウトボード側からグリースリップ46を通過した潤滑剤のインボード側への流出を阻止する。 Also, the grease lip 46 and the seal lip 47 act similarly to the grease lip 46 and the seal lip 47 of the sealing device 20 described above, respectively. That is, the grease lip 46 prevents the lubricant from flowing out from the inner space of the hub bearing 4 to the inboard side. In addition, the seal lip 47 backs up the grease lip 46 and prevents the lubricant that has passed through the grease lip 46 from flowing out from the outboard side to the inboard side.
 なお、グリースリップ46は、ハブベアリング4の内輪120の回転時にグリースリップ46がスリーブ31Aから離れないように、十分なグリースリップ46のスリーブ31Aへの締め付力(緊縛力)を発揮できる形状に形成されていることが好ましい。これにより、ハブベアリング4の内輪120の回転時に、特に高速回転時に、グリースリップ46の先端がスリーブ31Aから離れることを防止でき、ハブベアリング4の内部空間からインボード側への潤滑剤の漏れを抑制することができる。 The grease lip 46 has a shape capable of exhibiting a sufficient clamping force (bonding force) to the sleeve 31A so that the grease lip 46 does not separate from the sleeve 31A when the inner ring 120 of the hub bearing 4 rotates. is preferably formed. This prevents the tip of the grease lip 46 from separating from the sleeve 31A during rotation of the inner ring 120 of the hub bearing 4, particularly during high-speed rotation, and prevents lubricant from leaking from the inner space of the hub bearing 4 to the inboard side. can be suppressed.
 一方、シールリップ47は、ガータースプリング50によってスリーブ31Aへの締め付力(緊縛力)が高められているため、ハブベアリング4の内輪120の回転時に、特に高速回転時に、シールリップ47がスリーブ31Aから離れることが抑制されており、潤滑剤のインボード側への漏れを抑制することができる。 On the other hand, the garter spring 50 increases the tightening force (tightening force) of the seal lip 47 to the sleeve 31A. It is possible to suppress the leakage of the lubricant to the inboard side.
 以上のように、回転する内輪120に取り付けられた第2のシール部材65のサイドリップ68は、内輪120の回転速度が閾値より小さい場合には、剛性環42の接触面73に摺動可能に接触し、密封装置22の封止性能を確保する。すなわち、低速回転時において、サイドリップ68は、空間55に侵入した異物がハブベアリング4の内部空間に向けてさらに侵入しないように異物の侵入を阻止する。 As described above, the side lip 68 of the second seal member 65 attached to the rotating inner ring 120 is slidable on the contact surface 73 of the rigid ring 42 when the rotational speed of the inner ring 120 is lower than the threshold. contact to ensure the sealing performance of the sealing device 22 . That is, during low-speed rotation, the side lip 68 prevents foreign matter from entering the space 55 and further entering the inner space of the hub bearing 4 .
 一方、内輪120の回転速度が閾値より大きい場合には、第2のシール部材65のサイドリップ68は、サイドリップ68自身にかかる遠心力によって、剛性環42の接触面73から離れるように変形する。したがって、高速回転時において、密封装置22は、回転する内輪120にかかるトルクを低減し、また、サイドリップ68の摩耗、摩擦熱による温度の上昇を抑制する。 On the other hand, when the rotational speed of the inner ring 120 is higher than the threshold, the side lip 68 of the second seal member 65 is deformed away from the contact surface 73 of the rigid ring 42 by the centrifugal force acting on the side lip 68 itself. . Therefore, during high-speed rotation, the sealing device 22 reduces the torque applied to the rotating inner ring 120, and also suppresses wear of the side lip 68 and temperature rise due to frictional heat.
 なお、内輪120の高速回転時には、サイドリップ68が剛性環42の接触面73から離れるが、第2のシール部材65自体が高速で回転しているので、空間55の内部には径方向外側に向かう気流又は遠心力が生じ、空間55の内部に侵入した異物が間隙74,74aを通じて外部に排出される。ラビリンスリップ69が、図7に示すように、径方向外側かつインボード側に向かって斜めに延びている場合、上述のように侵入した異物が間隙74,74aを通じて外部に排出され易くすることができる。また、サイドリップ68の径方向内部の空間57からも気流又は遠心力によって異物がサイドリップ68と接触面73との間の間隙56を通じて、空間55に排出され、さらに間隙74,74aを通じて外部に排出される。 When the inner ring 120 rotates at a high speed, the side lip 68 separates from the contact surface 73 of the rigid ring 42, but since the second seal member 65 itself rotates at a high speed, the space 55 is radially outward. A directed air current or centrifugal force is generated, and foreign matter that has entered the space 55 is discharged to the outside through the gaps 74 and 74a. As shown in FIG. 7, if the labyrinth lip 69 extends diagonally outward in the radial direction and toward the inboard side, foreign matter that has entered as described above can be easily discharged to the outside through the gaps 74 and 74a. can. Foreign matter is discharged from the space 57 inside the side lip 68 in the radial direction by the airflow or centrifugal force through the gap 56 between the side lip 68 and the contact surface 73 to the space 55, and then to the outside through the gaps 74 and 74a. Ejected.
 次いで、本発明の第4の実施形態に係る密封装置23について説明する。本発明の第4の実施形態に係る密封装置23は、上述の本発明の第3の実施形態に係る密封装置22に対して、第1のシール部材及び第2のシール部材の構成が異なる。以下、密封装置23の構成について、密封装置22と同じ構成又は同様の機能を有する構成については同じ符号を付してその説明を省略し、異なる構成について説明する。 Next, a sealing device 23 according to a fourth embodiment of the invention will be described. A sealing device 23 according to the fourth embodiment of the present invention differs from the above-described sealing device 22 according to the third embodiment of the present invention in the configurations of the first sealing member and the second sealing member. Hereinafter, with respect to the configuration of the sealing device 23, the same reference numerals are given to the same configurations or configurations having the same functions as those of the sealing device 22, and the description thereof will be omitted, and the different configurations will be described.
 図8に示すように、環状の密封装置23は、上述の密封装置22の第1のシール部材70とは異なる第1のシール部材75と、密封装置22の第2のシール部材65とは異なる第2のシール部材80とを備えている。第1のシール部材75は、上述の密封装置22の第1のシール部材70の剛性環42と、第1のシール部材70の弾性環71とは異なる弾性環76とを有している。また、第2のシール部材80は、上述の密封装置22の第2のシール部材65の剛性環31とは異なる剛性環81と、第2のシール部材65の弾性環66とは異なる弾性環82とを有している。なお、図8においては、密封装置23の軸線xに対する一方の部分のみが示されている。また、図8において、密封装置23は、後述する使用状態における状態(配置)で示されている。 As shown in FIG. 8, the annular sealing device 23 has a first sealing member 75 different from the first sealing member 70 of the sealing device 22 described above and a second sealing member 65 of the sealing device 22. and a second sealing member 80 . The first seal member 75 has the rigid ring 42 of the first seal member 70 of the sealing device 22 described above and an elastic ring 76 different from the elastic ring 71 of the first seal member 70 . The second seal member 80 includes a rigid ring 81 different from the rigid ring 31 of the second seal member 65 of the sealing device 22 described above and an elastic ring 82 different from the elastic ring 66 of the second seal member 65 . and 8, only one portion of the sealing device 23 with respect to the axis x is shown. In addition, in FIG. 8, the sealing device 23 is shown in a state (arrangement) in use, which will be described later.
 図8に示すように、第1のシール部材75は、第2のシール部材80を径方向外側から覆うように配置される。このため、使用状態において、第2のシール部材80は、第1のシール部材75よりも径方向内側に固定される。また、第2のシール部材80の後述するフランジ81Bは、インボード側に面し、第1のシール部材75の円板部45は、アウトボード側に面する。 As shown in FIG. 8, the first sealing member 75 is arranged so as to cover the second sealing member 80 from the outside in the radial direction. Therefore, in use, the second seal member 80 is fixed radially inward of the first seal member 75 . Further, a later-described flange 81B of the second seal member 80 faces the inboard side, and the disk portion 45 of the first seal member 75 faces the outboard side.
 第1のシール部材75の弾性環76は、図8に示すように、円板部45の部分である内側端部72と、グリースリップ46と、シールリップ47が形成された円環部49とを有していない点で、密封装置22の第1のシール部材70の弾性環71と異なる。このため、第1のシール部材75は、ガータースプリング50を有していない。 The elastic ring 76 of the first seal member 75 comprises, as shown in FIG. It differs from the elastic ring 71 of the first sealing member 70 of the sealing device 22 in that it does not have a Therefore, the first seal member 75 does not have the garter spring 50 .
 第2のシール部材80の剛性環81は、剛性材料、例えば金属から形成されており、図8に示すように、密封装置22の第2のシール部材65の剛性環31のスリーブ31Aに対応する部分であるスリーブ81Aと、剛性環31のフランジ31Bに対応する部分であるフランジ81Bとを有している。剛性環81は、例えば図8に示すように、剛性環42と同様の形状を有しており、スリーブ81Aは、剛性環42の管状部44の部分と同様の形状を有しており、フランジ81Bは、剛性環42の円板部45の部分と同様の形状を有している。 The rigid ring 81 of the second sealing member 80 is made of a rigid material, such as metal, and corresponds to the sleeve 31A of the rigid ring 31 of the second sealing member 65 of the sealing device 22, as shown in FIG. It has a sleeve 81A which is a portion and a flange 81B which is a portion corresponding to the flange 31B of the rigid ring 31. The rigid ring 81 has a shape similar to that of the rigid ring 42, and the sleeve 81A has a shape similar to that of the tubular portion 44 of the rigid ring 42, as shown in FIG. 81B has the same shape as the disk portion 45 of the rigid ring 42 .
 第2のシール部材80の弾性環82は、弾性材料、例えばエラストマーで形成されている。弾性環82は、図8に示すように、剛性環81に取り付けられており、具体的には、弾性環82は、剛性環81の一部に密着しており、また、剛性環81の一部は、弾性環82に埋設されている。 The elastic ring 82 of the second seal member 80 is made of an elastic material such as elastomer. The elastic ring 82 is attached to the rigid ring 81, as shown in FIG. The portion is embedded in the elastic ring 82 .
 第2のシール部材80の弾性環82は、図8に示すように、剛性環81のフランジ81Bのアウトボード側の面、および剛性環81のスリーブ81Aの径方向外側の面に取り付けられている部分である基部83と、基部83から延びる部分であるサイドリップ68及びラビリンスリップ69とを有している。また、弾性環82は、図8に示すように、基部83から延びる部分であるシール突起84を有している。 As shown in FIG. 8, the elastic ring 82 of the second seal member 80 is attached to the outboard side surface of the flange 81B of the rigid ring 81 and the radially outer surface of the sleeve 81A of the rigid ring 81. It has a base 83 which is a portion, and side lips 68 and labyrinth lip 69 which are portions extending from the base 83 . The elastic ring 82 also has a seal projection 84 extending from the base portion 83, as shown in FIG.
 基部83は、軸線x周りに環状に延びており、径方向外側において、フランジ81Bの径方向外側の端部を覆うように形成されており、また、アウトボード側において、スリーブ81Aのアウトボード側の端部を覆うように形成されている。 The base portion 83 extends annularly around the axis x, and is formed so as to cover the radially outer end portion of the flange 81B on the radially outer side, and on the outboard side of the sleeve 81A. is formed to cover the end of the
 サイドリップ68は、図8に示すように、弾性環82の基部83のアウトボード側に面する面(面83a)から延びており、上述の密封装置22の第2のシール部材65のサイドリップ68と同様の形状を有しており、第1のシール部材75の剛性環42の接触面73に向けて延びている薄板状の弾性環82の部分である。サイドリップ68は、例えば図8に示すように、基部83に隣接する環状の厚い基部68aと、基部68aから径方向外側かつ接触面73に向けて斜めに延びて円錐台形状又は円錐筒状の形状を有する環状の薄い先端部68bとを有している。 The side lip 68 extends from the surface (surface 83a) facing the outboard side of the base portion 83 of the elastic ring 82, as shown in FIG. It is a portion of a thin plate-like elastic ring 82 that has the same shape as 68 and extends toward the contact surface 73 of the rigid ring 42 of the first sealing member 75 . For example, as shown in FIG. 8, the side lip 68 has an annular thick base portion 68a adjacent to the base portion 83 and a truncated cone shape or a conical tubular shape extending radially outward from the base portion 68a and obliquely toward the contact surface 73. and an annular thin tip 68b having a shape.
 後述する密封装置23の使用状態において、密封装置23の適用対象および第2のシール部材80の低速回転時(回転速度が閾値より小さい場合)には、サイドリップ68の先端部68bが、剛性環42の接触面73に摺動可能に接触するように、サイドリップ68は設計されている。一方、密封装置23の適用対象および第2のシール部材80の高速回転時(回転速度が閾値より大きい場合)には、上述の密封装置22のサイドリップ68と同様に、サイドリップ68の先端部68bが、剛性環42の接触面73から離れるように変形するように、サイドリップ68は設計されている。なお、サイドリップ68は、密封装置23の適用対象および第2のシール部材80の高速回転時に、先端部68bが、剛性環42の接触面73から離れない範囲で接触面73から離れる方向に移動するように、設計されていてもよい。 In the state of use of the sealing device 23, which will be described later, when the object to which the sealing device 23 is applied and the second sealing member 80 rotates at a low speed (when the rotation speed is smaller than the threshold value), the tip portion 68b of the side lip 68 is moved to the rigid ring. The side lip 68 is designed to slidably contact the contact surface 73 of 42 . On the other hand, when the sealing device 23 is applied and the second sealing member 80 rotates at high speed (when the rotation speed is greater than the threshold value), the tip portion of the side lip 68 is Side lip 68 is designed such that 68b deforms away from contact surface 73 of rigid ring 42 . When the sealing device 23 is applied and the second sealing member 80 rotates at high speed, the side lip 68 moves away from the contact surface 73 of the rigid ring 42 within a range in which the tip portion 68b does not move away from the contact surface 73. It may be designed to
 また、図8に示すように、第2のシール部材80のフランジ81Bの径方向外側端部を覆う基部83の部分である外側端部83bは、第1のシール部材75の管状部44の弾性環76の有するラビリンス受部71aに径方向において間隔を空けて対向するようになっている。このため、基部83の外側端部83bと管状部44のラビリンス受部71aとの間には、間隙74が形成される。 Further, as shown in FIG. 8, the outer end portion 83b, which is the portion of the base portion 83 that covers the radially outer end portion of the flange 81B of the second seal member 80, is the elastic portion of the tubular portion 44 of the first seal member 75. It faces the labyrinth receiving portion 71a of the ring 76 with a gap in the radial direction. Therefore, a gap 74 is formed between the outer end portion 83 b of the base portion 83 and the labyrinth receiving portion 71 a of the tubular portion 44 .
 ラビリンスリップ69は、図8に示すように、基部83の外側端部83bからラビリンス受部71aに向かって延びており、ラビリンスリップ69の先端部69aは、ラビリンス受部71aに径方向において間隔を空けて対向するようになっている。このように、間隙74において、ラビリンスリップ69の先端部69aとラビリンス受部71aとの間には、間隙74をさらに狭める環状の間隙74aが形成されている。間隙74及び間隙74aは、ラビリンスシールを形成する。 As shown in FIG. 8, the labyrinth lip 69 extends from the outer end 83b of the base 83 toward the labyrinth receiving portion 71a. They are facing each other with a space between them. Thus, in the gap 74, an annular gap 74a is formed between the tip 69a of the labyrinth lip 69 and the labyrinth receiving portion 71a to further narrow the gap 74. As shown in FIG. Gap 74 and gap 74a form a labyrinth seal.
 シール突起84は、軸線x周りに環状の部分であり、図8に示すように、スリーブ81Aのアウトボード側端部を覆う基部83の部分であるアウトボード側端部83cから延びる環状の突起である。シール突起84は、アウトボード側端部83cから、第1のシール部材75の剛性環42の円板部45における径方向内側の端縁である内端縁45bに向かって延びている。図8に示すように、剛性環42の内端縁45bは、基部83のアウトボード側端部83cに対して、例えば径方向外側かつアウトボード側に位置するようになっており、シール突起84は、アウトボード側端部83cから、径方向外側かつアウトボード側に向かって斜めに延びている。また、シール突起84は、シール突起84の先端側の部分(先端部84a)が剛性環42の内端縁45bに接触するような形状に形成されている。 The seal projection 84 is a ring-shaped portion around the axis x, and as shown in FIG. be. The seal projection 84 extends from the outboard side end portion 83 c toward the inner edge 45 b that is the radially inner edge of the disk portion 45 of the rigid ring 42 of the first seal member 75 . As shown in FIG. 8, the inner edge 45b of the rigid ring 42 is positioned, for example, radially outward and on the outboard side with respect to the outboard side end portion 83c of the base portion 83. extends obliquely from the outboard side end 83c radially outward and toward the outboard side. Further, the sealing projection 84 is formed in such a shape that the tip portion (tip portion 84 a ) of the sealing projection 84 contacts the inner edge 45 b of the rigid ring 42 .
 次いで、上述の構成を有する密封装置23の作用について説明する。密封装置23は、適用対象に取り付けられて使用状態になる。密封装置23の適用対象は、例えばハブベアリングであり、密封装置23の適用対象のハブベアリングは、内輪回転型のハブベアリングである。密封装置23は、例えば密封装置22と同様に、上述の密封装置21が取り付けられるハブベアリング4に取り付けられる(図6参照)。なお、密封装置23が取り付けられたハブベアリング4の図示は省略されている。 Next, the action of the sealing device 23 having the above configuration will be described. The sealing device 23 is attached to the application and is ready for use. The application target of the sealing device 23 is, for example, a hub bearing, and the hub bearing to which the sealing device 23 is applied is an inner ring rotation type hub bearing. The sealing device 23 is mounted, for example, like the sealing device 22, on the hub bearing 4 to which the sealing device 21 described above is mounted (see FIG. 6). The illustration of the hub bearing 4 to which the sealing device 23 is attached is omitted.
 密封装置23は、密封装置22と同様に、ハブベアリング4のインボード側開口部126に取り付けられる。具体的には、外輪130のインボード側の端部130Aに、密封装置23の第1のシール部材75の管状部44が取り付けられ、また、内輪120の内側輪121のインボード側の端部121Aに、密封装置23の第2のシール部材80のスリーブ81Aが取り付けられ、密封装置23はハブベアリング4に取り付けられる(図6,8参照)。第1のシール部材75の管状部44は、具体的には、外輪130の端部130Aに締り嵌め方式で嵌め入れられ、第2のシール部材80のスリーブ81Aは、具体的には、内側輪121の端部121Aに締り嵌め方式で嵌め入れられる。ハブベアリング4に取り付けられた密封装置23の軸線xは、ハブベアリング4の中心軸線Axに一致又は略一致する。 The sealing device 23 is attached to the inboard side opening 126 of the hub bearing 4 in the same manner as the sealing device 22 . Specifically, the tubular portion 44 of the first sealing member 75 of the sealing device 23 is attached to the inboard side end portion 130A of the outer ring 130, and the inboard side end portion of the inner ring 121 of the inner ring 120 is attached. The sleeve 81A of the second seal member 80 of the sealing device 23 is attached to 121A, and the sealing device 23 is attached to the hub bearing 4 (see FIGS. 6 and 8). The tubular portion 44 of the first sealing member 75 is specifically fitted to the end portion 130A of the outer ring 130 in an interference fit, and the sleeve 81A of the second sealing member 80 is specifically fitted to the inner ring. The end portion 121A of 121 is fitted by an interference fit method. The axis x of the sealing device 23 attached to the hub bearing 4 coincides or substantially coincides with the central axis Ax of the hub bearing 4 .
 上述のように、密封装置23はハブベアリング4に固定される。第1のシール部材75は、静止した外輪130に固定され、回転しない固定シール部材である。一方、第2のシール部材80は、回転する内輪120に固定され、回転する回転シール部材である。ハブベアリング4において密封装置23は、内輪120の回転速度に応じて異なった作用をする。 The sealing device 23 is fixed to the hub bearing 4 as described above. The first seal member 75 is a stationary seal member that is fixed to the stationary outer ring 130 and does not rotate. On the other hand, the second seal member 80 is a rotary seal member that is fixed to the rotating inner ring 120 and rotates. The sealing device 23 in the hub bearing 4 acts differently depending on the rotational speed of the inner ring 120 .
 具体的には、内輪120および第2のシール部材80の低速回転時(回転速度が閾値より小さい場合)には、図8に示すように、サイドリップ68は、密封装置22のサイドリップ68と同様に作用し、第1のシール部材75の剛性環42の接触面73に接触し、空間55の内部に侵入した異物がハブベアリング4の内部空間に向けてさらに侵入しないように異物の侵入を阻止する役割を有する。低速回転時とは、内輪120および第2のシール部材80の回転が停止している時を含む。剛性環42の接触面73から第2のシール部材80に与えられるトルクを低減するため、サイドリップ68にはグリースがコートされてもよい。このグリースは、典型的には玉10,12、内輪120、外輪130を潤滑するグリースとは別種である。 Specifically, when the inner ring 120 and the second seal member 80 rotate at a low speed (when the rotation speed is smaller than the threshold value), the side lip 68 of the sealing device 22 and the side lip 68 of the sealing device 22 as shown in FIG. It works similarly to contact the contact surface 73 of the rigid ring 42 of the first seal member 75 to prevent foreign matter from entering the space 55 from further entering the inner space of the hub bearing 4 . It has a deterrent role. The time of low speed rotation includes the time when the rotation of the inner ring 120 and the second seal member 80 is stopped. The side lip 68 may be coated with grease to reduce the torque imparted to the second seal member 80 from the contact surface 73 of the rigid ring 42 . This grease is different from the grease that typically lubricates the balls 10, 12, inner ring 120, and outer ring 130.
 一方、内輪120および第2のシール部材80の高速回転時(回転速度が閾値より大きい場合)には、図8に点線で示すように、サイドリップ68、特に先端部68bは、密封装置22のサイドリップ68と同様に作用し、サイドリップ68自身にかかる遠心力によって、第1のシール部材75の剛性環42の接触面73から離れるよう変形する。このため、密封装置22と同様に、内輪120および第2のシール部材80の高速回転時に、サイドリップ68の先端部68bと剛性環42の接触面73との間に、円環状の間隙56が設けられる。これにより、内輪120の高速回転時に、サイドリップ68と接触面73との間の摺動抵抗をなくすことができ、回転する内輪120にかかるトルクを小さくすることができる。また、サイドリップ68の摩耗、摩擦熱による温度の上昇を抑制することができる。 On the other hand, when the inner ring 120 and the second seal member 80 rotate at high speed (when the rotation speed is greater than the threshold value), the side lip 68, particularly the tip portion 68b, of the sealing device 22, as indicated by the dotted line in FIG. Acting like the side lip 68 , the centrifugal force on the side lip 68 itself deforms it away from the contact surface 73 of the rigid ring 42 of the first sealing member 75 . Therefore, similarly to the sealing device 22, when the inner ring 120 and the second sealing member 80 rotate at high speed, the annular gap 56 is formed between the tip portion 68b of the side lip 68 and the contact surface 73 of the rigid ring 42. be provided. As a result, sliding resistance between the side lip 68 and the contact surface 73 can be eliminated when the inner ring 120 rotates at high speed, and the torque applied to the rotating inner ring 120 can be reduced. Also, it is possible to suppress the wear of the side lip 68 and the increase in temperature due to frictional heat.
 また、図8に示すように、第2のシール部材80のラビリンスリップ69と、第1のシール部材75の管状部44のラビリンス受部71aとの間には、環状の間隙74,74aが設けられており、密封装置22の間隙74,74aと同様に、間隙74,74aはラビリンスシールとして機能する。このため、ハブベアリング4の外部から密封装置23の内部の空間55に異物が侵入することが防止されている。このように、密封装置23は、間隙74,74aによっても、ハブベアリング4の内部空間に異物が侵入することを抑制することができる。また、ハブベアリング4の外部に潤滑剤が流出することを抑制することができる。 8, annular gaps 74 and 74a are provided between the labyrinth lip 69 of the second seal member 80 and the labyrinth receiving portion 71a of the tubular portion 44 of the first seal member 75. and, like the gaps 74, 74a of the sealing device 22, the gaps 74, 74a function as labyrinth seals. Therefore, foreign matter is prevented from entering the space 55 inside the sealing device 23 from the outside of the hub bearing 4 . In this manner, the sealing device 23 can prevent foreign matter from entering the inner space of the hub bearing 4 by the gaps 74 and 74a. In addition, it is possible to prevent the lubricant from flowing out of the hub bearing 4 .
 また、シール突起84の先端部84aは、第1のシール部材75の剛性環42の内端縁45bに接触しており、シール突起84は、第1のシール部材75の剛性環42の内端縁45bと、第2のシール部材80の弾性環82のアウトボード側端部83cとの間の環状の間隙を塞いでいる。このため、シール突起84は、ハブベアリング4の内部空間からインボード側への潤滑剤の流出を阻止する。また、シール突起84は、ハブベアリング4の内部空間への異物の侵入を阻止する。 Further, the tip portion 84a of the seal projection 84 is in contact with the inner edge 45b of the rigid ring 42 of the first seal member 75, and the seal projection 84 contacts the inner end of the rigid ring 42 of the first seal member 75. It closes the annular gap between the edge 45b and the outboard side end 83c of the elastic ring 82 of the second seal member 80 . Therefore, the seal projection 84 prevents the lubricant from flowing out from the inner space of the hub bearing 4 to the inboard side. Also, the seal projection 84 prevents foreign matter from entering the internal space of the hub bearing 4 .
 シール突起84の先端部84aは、剛性環42の内端縁45bに径方向内側から接触している。このため、ハブベアリング4の内輪120の回転によってシール突起84に遠心力がかかると、この遠心力によって、シール突起84の先端部84aは、剛性環42の内端縁45bにさらに押し付けられる。このため、ハブベアリング4の内輪120の回転時に、特に高速回転時に、シール突起84の先端部84aが剛性環42の内端縁45bから離れることを防止でき、ハブベアリング4の内部空間からインボード側への潤滑剤の漏れをさらに抑制することができる。 The tip 84a of the seal projection 84 is in contact with the inner edge 45b of the rigid ring 42 from the inside in the radial direction. Therefore, when the inner ring 120 of the hub bearing 4 rotates and a centrifugal force is applied to the seal projection 84 , the distal end portion 84 a of the seal projection 84 is further pressed against the inner edge 45 b of the rigid ring 42 . Therefore, when the inner ring 120 of the hub bearing 4 rotates, particularly during high-speed rotation, it is possible to prevent the tip 84a of the seal projection 84 from separating from the inner edge 45b of the rigid ring 42. The leakage of the lubricant to the side can be further suppressed.
 以上のように、回転する内輪120に取り付けられた第2のシール部材80のサイドリップ68は、内輪120の回転速度が閾値より小さい場合には、剛性環42の接触面73に摺動可能に接触し、密封装置23の封止性能を確保する。すなわち、低速回転時において、サイドリップ68は、空間55に侵入した異物がハブベアリング4の内部空間に向けてさらに侵入しないように異物の侵入を阻止する。 As described above, the side lip 68 of the second seal member 80 attached to the rotating inner ring 120 is slidable on the contact surface 73 of the rigid ring 42 when the rotational speed of the inner ring 120 is less than the threshold. to ensure the sealing performance of the sealing device 23. That is, during low-speed rotation, the side lip 68 prevents foreign matter from entering the space 55 and further entering the inner space of the hub bearing 4 .
 一方、内輪120の回転速度が閾値より大きい場合には、第2のシール部材80のサイドリップ68は、サイドリップ68自身にかかる遠心力によって、剛性環42の接触面73から離れるように変形する。したがって、高速回転時において、密封装置23は、回転する内輪120にかかるトルクを低減し、また、サイドリップ68の摩耗、摩擦熱による温度の上昇を抑制する。 On the other hand, when the rotational speed of the inner ring 120 is higher than the threshold value, the side lip 68 of the second seal member 80 is deformed away from the contact surface 73 of the rigid ring 42 by the centrifugal force acting on the side lip 68 itself. . Therefore, during high-speed rotation, the sealing device 23 reduces the torque applied to the rotating inner ring 120, and suppresses temperature rise due to wear of the side lip 68 and frictional heat.
 なお、内輪120の高速回転時には、サイドリップ68が剛性環42の接触面73から離れるが、第2のシール部材80自体が高速で回転しているので、空間55の内部には径方向外側に向かう気流又は遠心力が生じ、空間55の内部に侵入した異物が間隙74,74aを通じて外部に排出される。ラビリンスリップ69が、図8に示すように、径方向外側かつインボード側に向かって斜めに延びている場合、上述のように侵入した異物が間隙74,74aを通じて外部に排出され易くすることができる。また、サイドリップ68の径方向内部の空間57からも気流又は遠心力によって異物がサイドリップ68と接触面73との間の間隙56を通じて、空間55に排出され、さらに間隙74,74aを通じて外部に排出される。 When the inner ring 120 rotates at a high speed, the side lip 68 separates from the contact surface 73 of the rigid ring 42. However, since the second seal member 80 itself rotates at a high speed, the inside of the space 55 is radially outward. A directed air current or centrifugal force is generated, and foreign matter that has entered the space 55 is discharged to the outside through the gaps 74 and 74a. As shown in FIG. 8, if the labyrinth lip 69 extends diagonally outward in the radial direction and toward the inboard side, foreign matter that has entered as described above can be easily discharged to the outside through the gaps 74 and 74a. can. Foreign matter is discharged from the space 57 inside the side lip 68 in the radial direction by the airflow or centrifugal force through the gap 56 between the side lip 68 and the contact surface 73 to the space 55, and then to the outside through the gaps 74 and 74a. Ejected.
 なお、サイドリップ48,62,68が夫々変形するハブベアリング1,3,4の高速回転時の回転速度の閾値は、例えば、サイドリップ48,62,68の基部51,62a,68aや先端部52,62b,68bの形状や、弾性環41,61,66,82の弾性材料の特性等によって調整することができる。この基部51,62a,68aや先端部52,62b,68bの形状には、例えば、基部51,62a,68aや先端部52,62b,68bの厚さや硬さがある。弾性材料の特性には、例えば、弾性材料の弾性率がある。また、サイドリップ48,62,68が夫々変形するハブベアリング1,3,4の高速回転時の回転速度の閾値は、中心軸線Ax方向における第1のシール部材30,70,75と第2のシール部材40,60,65,80との距離(間隔)によっても調整することができる。 Note that the rotational speed thresholds of the hub bearings 1, 3, 4 at which the side lips 48, 62, 68 are deformed at high speeds are, for example, It can be adjusted by the shape of 52, 62b, 68b, the characteristics of the elastic material of the elastic rings 41, 61, 66, 82, and the like. The shapes of the base portions 51, 62a, 68a and the tip portions 52, 62b, 68b include, for example, the thickness and hardness of the base portions 51, 62a, 68a and the tip portions 52, 62b, 68b. Properties of the elastic material include, for example, the elastic modulus of the elastic material. Further, the threshold values of the rotational speeds of the hub bearings 1, 3, 4 at which the side lips 48, 62, 68 are respectively deformed during high-speed rotation are the first seal members 30, 70, 75 and the second It can also be adjusted by the distance (interval) to the seal members 40 , 60 , 65 , 80 .
 以上、本発明の好ましい実施形態を参照しながら本発明を図示して説明したが、当業者にとって特許請求の範囲に記載された発明の範囲から逸脱することなく、形式および詳細の変更が可能であることが理解されるであろう。このような変更、改変および修正は本発明の範囲に包含されるはずである。 Although the invention has been illustrated and described with reference to preferred embodiments thereof, it will be appreciated by those skilled in the art that changes in form and detail can be made without departing from the scope of the invention as set forth in the claims. One thing will be understood. Such changes, alterations and modifications are intended to fall within the scope of the present invention.
 例えば、複数のサイドリップを設けてもよい。 For example, multiple side lips may be provided.
 空間55には、サイドリップ48,62,68側への異物の侵入を減少させるための突起を設けてもよい。突起は、第1のシール部材30,70,75に形成してもよいし、第2のシール部材40,60,65,に形成してもよい。 A protrusion may be provided in the space 55 to reduce the entry of foreign matter into the side lips 48, 62, 68. The protrusions may be formed on the first sealing members 30, 70, 75 or may be formed on the second sealing members 40, 60, 65.
 1,3,4…ハブベアリング、2…孔、6,120…内輪(内側部材)、8,130…外輪(外側部材)、20,21,22,23…密封装置、30,70,75…第1のシール部材、31,81…剛性環、31A,81A…スリーブ、31Ap…部分、31B,81B…フランジ、31Bt…外端縁、40,60,65,80…第2のシール部材、41,61,66,82…弾性環、42…剛性環、44…管状部、44a…端部、45…円板部、45a…外端縁、45b…内端縁、46…グリースリップ(ラジアルリップ)、47…シールリップ(ラジアルリップ)、48,62,68…サイドリップ、49…円環部、50…ガータースプリング、51,62a,68a…基部、52,62b,68b…先端部、54,63,74,74a…間隙、67,83…基部、67a,83a…面、67b,83b…外側端部、69…ラビリンスリップ、69a…先端部、71,76…弾性環、71a…ラビリンス受部、72…内側端部、73…接触面、83c…アウトボード側端部、84…シール突起、84a…先端部、100…インホイールモータユニット、101…外側ケーシング、101a…端部、101b…取付面、102…内側ケーシング、102a…筒部、102b…円板部、102c…取付面、103…モータジェネレータ、104…ロータ、105…ステータ、110…ブレーキディスク、121…内側輪、121A…端部、122…ハブ輪、123…軸部、124…ハブフランジ、126…インボード側開口部、127…アウトボード側開口部、130A…端部、131…貫通孔、140…他の密封装置、Ax…中心軸線、x…軸線
 
1, 3, 4... Hub bearing 2... Hole 6, 120... Inner ring (inner member) 8, 130... Outer ring (outer member) 20, 21, 22, 23... Sealing device 30, 70, 75... First sealing member 31, 81... rigid ring 31A, 81A... sleeve 31Ap... portion 31B, 81B... flange 31Bt... outer edge 40, 60, 65, 80... second sealing member 41 , 61, 66, 82... Elastic ring 42... Rigid ring 44... Tubular part 44a... End part 45... Disk part 45a... Outer edge 45b... Inner edge 46... Grease lip (radial lip ), 47... Seal lip (radial lip), 48, 62, 68... Side lip, 49... Annular part, 50... Garter spring, 51, 62a, 68a... Base part, 52, 62b, 68b... Tip part, 54, 63, 74, 74a... Gap 67, 83... Base part 67a, 83a... Surface 67b, 83b... Outer end part 69... Labyrinth lip 69a... Tip part 71, 76... Elastic ring 71a... Labyrinth receiving part , 72... Inner end 73... Contact surface 83c... Outboard side end 84... Seal projection 84a... Tip part 100... In-wheel motor unit 101... Outer casing 101a... End 101b... Mounting Surface 102... Inner casing 102a... Cylindrical part 102b... Disk part 102c... Mounting surface 103... Motor generator 104... Rotor 105... Stator 110... Brake disc 121... Inner ring 121A... End , 122...Hub ring, 123...Axle, 124...Hub flange, 126...Inboard side opening, 127...Outboard side opening, 130A...End, 131...Through hole, 140...Other sealing device, Ax ... central axis, x ... axis

Claims (8)

  1.  固定された内側部材と回転する外側部材との間に配置され、前記内側部材と前記外側部材との間の間隙を封止する密封装置であって、
     前記内側部材に取り付けられたスリーブと、前記スリーブから径方向外側に広がるフランジを有する第1のシール部材と、
     前記フランジの径方向外側に配置されて前記外側部材に取り付けられた管状部と、前記管状部から径方向内側に広がり前記フランジに対向する円板部と、前記円板部の径方向内側に配置されて前記スリーブに摺動可能に接触するラジアルリップと、前記円板部から前記フランジに向けて延びるサイドリップを有する第2のシール部材を有し、
     前記第2のシール部材の前記サイドリップは、前記外側部材の回転速度が閾値より小さい場合には、前記フランジに摺動可能に接触し、前記外側部材の回転速度が閾値より大きい場合には、前記フランジから離れるよう変形することを特徴とする密封装置。
    A sealing device disposed between a fixed inner member and a rotating outer member for sealing a gap between the inner member and the outer member, comprising:
    a sleeve attached to the inner member and a first sealing member having a flange extending radially outwardly from the sleeve;
    A tubular portion disposed radially outward of the flange and attached to the outer member, a disk portion extending radially inward from the tubular portion and facing the flange, and disposed radially inward of the disk portion. a second seal member having a radial lip that is formed to slidably contact the sleeve and a side lip that extends from the disk portion toward the flange;
    the side lip of the second seal member slidably contacts the flange when the rotational speed of the outer member is less than a threshold; and when the rotational speed of the outer member is greater than the threshold, A sealing device, characterized in that it deforms away from said flange.
  2.  回転する内側部材と固定された外側部材との間に配置され、前記内側部材と前記外側部材との間の間隙を封止する密封装置であって、
     前記外側部材に取り付けられる第1のシール部材と、
     前記内側部材に取り付けられる第2のシール部材とを備え、
     前記第1のシール部材は、剛性材料から形成された軸線周りに環状の部材である第1の剛性環を有しており、
     前記第2のシール部材は、剛性材料から形成された前記軸線周りに環状の部材である第2の剛性環と、弾性材料から形成された前記軸線周りに環状の部材である第2の弾性環とを有しており、
     前記第2のシール部材の前記第2の弾性環は、前記軸線に沿って延びる前記軸線周りに環状の部分であるサイドリップを有しており、
     前記第1のシール部材の前記第1の剛性環は、前記サイドリップの先端部が接触するようになっており、
     前記第2のシール部材の前記サイドリップは、前記内側部材の回転速度が閾値より小さい場合には、前記第1のシール部材の前記第1の剛性環に摺動可能に接触し、前記内側部材の回転速度が閾値より大きい場合には、前記第1のシール部材の前記第1の剛性環から離れる方向に移動するよう変形することを特徴とする密封装置。
    A sealing device disposed between a rotating inner member and a stationary outer member for sealing a gap between the inner member and the outer member, comprising:
    a first sealing member attached to the outer member;
    a second seal member attached to the inner member;
    The first sealing member has a first rigid ring that is an annular member around an axis formed of a rigid material,
    The second sealing member includes a second rigid ring that is an annular member formed of a rigid material around the axis, and a second elastic ring that is an annular member formed of an elastic material around the axis. and
    The second elastic ring of the second sealing member has a side lip which is an annular portion around the axis extending along the axis,
    The first rigid ring of the first sealing member is in contact with the tip of the side lip,
    The side lip of the second seal member slidably contacts the first rigid ring of the first seal member and the inner member when the rotation speed of the inner member is less than a threshold value. is greater than a threshold value, the sealing device deforms so as to move away from the first rigid ring of the first sealing member.
  3.  前記第2のシール部材の前記サイドリップは、前記内側部材の回転速度が閾値より大きい場合には、前記第1のシール部材の前記第1の剛性環から離れるよう変形することを特徴とする請求項2に記載の密封装置。 The side lip of the second seal member deforms away from the first rigid ring of the first seal member when the rotational speed of the inner member is greater than a threshold. 3. The sealing device according to item 2.
  4.  前記第1のシール部材と前記第2のシール部材とは、前記サイドリップよりも前記内側部材と前記外側部材との間の前記間隙の側に、環状の第1の間隙を形成しており、また、前記サイドリップよりも前記内側部材と前記外側部材との間の前記間隙から離れる側に、環状の第2の間隙を形成していることを特徴とする請求項2又は3に記載の密封装置。 The first seal member and the second seal member form an annular first gap closer to the gap between the inner member and the outer member than the side lip, 4. The seal according to claim 2, further comprising an annular second gap formed on the side of the side lip away from the gap between the inner member and the outer member. Device.
  5.  前記第2の弾性環は、前記第2の間隙に向かって突出してラビリンスシールを形成する前記軸線周りに環状の部分であるラビリンスリップを有していることを特徴とする請求項4に記載の密封装置。 5. A labyrinth lip according to claim 4, wherein said second elastic ring has a labyrinth lip which is an annular portion about said axis projecting towards said second gap to form a labyrinth seal. sealing device.
  6.  前記第1のシール部材は、弾性材料から形成された前記軸線周りに環状の部材である第1の弾性環を有しており、
     前記第1の弾性環は、前記第1の間隙を閉塞する部分である前記軸線周りに環状のシールリップを有していることを特徴とする請求項4に記載の密封装置。
    The first seal member has a first elastic ring that is an annular member formed of an elastic material around the axis,
    5. The sealing device according to claim 4, wherein said first elastic ring has a ring-shaped seal lip around said axis which is a portion that closes said first gap.
  7.  前記第2の弾性環は、前記第1の間隙を閉塞する部分である前記軸線周りに環状のシール突起を有しており、
     前記シール突起は、前記軸線に沿って突出しており、前記軸線の側から前記第1の剛性環に接触するように形成されていることを特徴とする請求項4に記載の密封装置。
    The second elastic ring has an annular seal projection around the axis line that closes the first gap,
    5. The sealing device according to claim 4, wherein the seal projection protrudes along the axis and is formed to contact the first rigid ring from the axis side.
  8.  前記第1の間隙はラビリンスシールを形成し、前記第2の間隙はラビリンスシールを形成することを特徴とする請求項4に記載の密封装置。
     
    5. The sealing device of claim 4, wherein said first gap forms a labyrinth seal and said second gap forms a labyrinth seal.
PCT/JP2022/020816 2021-05-20 2022-05-19 Sealing device WO2022244839A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001304278A (en) * 1999-10-08 2001-10-31 Nsk Ltd Sealed type bearing device
WO2006085651A1 (en) * 2005-02-14 2006-08-17 Nsk Ltd. Hub unit bearing
JP2010159792A (en) * 2009-01-07 2010-07-22 Ntn Corp Bearing device for wheel
JP2017133532A (en) * 2016-01-25 2017-08-03 株式会社ジェイテクト Bearing device
WO2020090484A1 (en) * 2018-10-31 2020-05-07 Ntn株式会社 Rolling bearing with pulley

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001304278A (en) * 1999-10-08 2001-10-31 Nsk Ltd Sealed type bearing device
WO2006085651A1 (en) * 2005-02-14 2006-08-17 Nsk Ltd. Hub unit bearing
JP2010159792A (en) * 2009-01-07 2010-07-22 Ntn Corp Bearing device for wheel
JP2017133532A (en) * 2016-01-25 2017-08-03 株式会社ジェイテクト Bearing device
WO2020090484A1 (en) * 2018-10-31 2020-05-07 Ntn株式会社 Rolling bearing with pulley

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