WO2012063506A1 - Sealing device - Google Patents

Sealing device Download PDF

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Publication number
WO2012063506A1
WO2012063506A1 PCT/JP2011/058504 JP2011058504W WO2012063506A1 WO 2012063506 A1 WO2012063506 A1 WO 2012063506A1 JP 2011058504 W JP2011058504 W JP 2011058504W WO 2012063506 A1 WO2012063506 A1 WO 2012063506A1
Authority
WO
WIPO (PCT)
Prior art keywords
lip
sealing element
sleeve
side sealing
sealing device
Prior art date
Application number
PCT/JP2011/058504
Other languages
French (fr)
Japanese (ja)
Inventor
小林　直人
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
Publication of WO2012063506A1 publication Critical patent/WO2012063506A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • F16J15/3264—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals the elements being separable from each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting region
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7859—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element
    • F16C33/7863—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element mounted to the inner race, e.g. a flinger to use centrifugal effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7859—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element
    • F16C33/7866—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a further sealing element with sealing lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
    • F16C33/7883—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7889—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to an inner race and extending toward the outer race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the present invention relates to a sealing device that prevents dust and muddy water from entering a bearing or the like in an automobile, a general machine, an industrial machine, etc., and performs sealing by swinging off a rotating side sealing element.
  • FIG. 8 is a one-side cross-sectional view showing a typical prior art of this type of sealing device cut along a plane passing through the axis O
  • FIG. 9 is a multi-pole magnetization of a magnetic encoder on a rotary-side sealing element.
  • 1 is a half sectional view showing a typical prior art of a sealing device provided with a disk by cutting along a plane passing through an axis O.
  • the sealing device shown in FIG. 8 or FIG. 9 is fitted to the outer periphery of the stationary ring sealing element 110 attached to the inner periphery of the outer ring 101 (stationary side) of the bearing 100 and the inner ring (rotation side) 102 of the bearing 100, for example.
  • a metal rotating side sealing element 120 comprising a flange 122 extending from one end of the sleeve 121 and a thrust strip 111 provided on the stationary side sealing element 110 slid on the flange 122 of the rotating side sealing element 120.
  • a radial lip 112 and a grease lip 113 which are movably brought into close contact with each other and are provided on the inner side of the thrust strip 111 on the stationary side sealing element 110 slide on the outer peripheral surface of the sleeve 121 of the rotary side sealing element 120. Be as close as possible.
  • the outer surface of the flange 122 of the rotary side sealing element 120 is formed into a disk shape with a rubber material or a synthetic resin material mixed with fine powder of magnetic material and has a predetermined circumferential direction.
  • a multi-pole magnetized disk (pulsar ring) 130 in which N poles and S poles are alternately magnetized at a pitch is integrally provided.
  • This multi-pole magnetized disk 130 constitutes a magnetic encoder together with a magnetic sensor (not shown) arranged oppositely in a non-rotating state on the outside thereof.
  • the sealing device shown in FIG. 8 or FIG. 9 has a swing-off action due to the centrifugal force of the flange 122 that rotates integrally with the inner ring 102 at the intimate sliding portion of the flange 122 of the rotating side sealing element 120 and the thrust strip 111. Intrusion of dust, muddy water, and the like from the outside A of the bearing 100 is prevented.
  • the sleeve 121 of the rotation-side sealing element 120 is in contact with the outer peripheral surface of the inner ring 102 with metals, so that muddy water or the like of the outer A is caused between the sleeve 121 and the inner ring 102. There was a risk of entering the internal space B of the bearing 100 from a minute gap between the fitting surfaces.
  • the present invention has been made in view of the above points, and a technical problem thereof is a sealing device that performs sealing by swinging off by rotation of a seal flange of a rotating side sealing element.
  • the object is to prevent inconvenience due to muddy water or the like entering from the fitting portion with the rotating member to which the rotating side sealing element is attached.
  • a sealing device includes a stationary side sealing element attached to a stationary member and having a first lip and a second lip, and the stationary member.
  • a rotation-side sealing element having a sleeve fitted to the rotation member on the inner diameter side and a seal flange extending from an end thereof and slidably in contact with the first lip; and the second lip is attached to the rotation member
  • the sleeve is fitted in a slidable manner, and the sleeve is fitted on a cylindrical surface formed on the rotating member so as to be located outside and on the inner diameter side of the close sliding portion with the second lip.
  • the sealing device according to the first aspect, wherein the seal flange is provided between the close sliding portion of the first lip and the second lip and the fitting portion of the sleeve. It is in contact with the end face.
  • a non-contact seal portion is formed in which the outer diameter portion of the seal flange and the stationary member are closely opposed to each other.
  • the sealing device is the structure according to any one of the first to third aspects, wherein a multi-pole magnetized disk is integrally provided on the outer surface of the seal flange.
  • the sealing device of the first aspect of the present invention even if an external fluid or the like enters from the fitting surface of the sleeve of the rotating member and the rotating side sealing element, the intruding fluid is separated from the second lip of the stationary side sealing element.
  • the intimate sliding portion with the rotating member prevents intrusion from the inside, and the first lip of the stationary side sealing element and the sealing flange closely slide with each other by the swinging action caused by the rotation of the sealing flange of the rotating side sealing element. Since it is discharged to the outside of the part, it has an excellent sealing effect.
  • the sealing device of the second aspect of the present invention even if an external fluid or the like enters from the fitting surface of the sleeve of the rotating member and the rotating side sealing element, the intruding fluid is not formed between the seal flange and the end surface of the rotating member. Since it is sealed at the abutting portion, it becomes difficult to reach the intimate sliding portion between the second lip of the stationary side sealing element and the rotating member, so that in addition to the effect of the first aspect, a more excellent sealing effect is achieved.
  • the non-contact seal portion between the outer diameter portion of the seal flange and the stationary member allows the external fluid or the like to flow between the first lip of the stationary side sealing element and the rotary side sealing element. Therefore, in addition to the effect of the first or second aspect, a further excellent sealing effect can be obtained.
  • the sealing device of the fourth aspect of the present invention since the radial width of the seal flange is large, the magnetized area of the multipolar magnetized disk provided on the outer surface thereof can be increased. In addition to the effect of 3, excellent rotation detection accuracy can be obtained.
  • FIG. 1 is a half sectional view showing a first preferred embodiment of a sealing device according to the present invention by cutting along a plane passing through an axis O.
  • FIG. FIG. 5 is a half sectional view showing a second preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O;
  • FIG. 6 is a half sectional view showing a third preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O;
  • FIG. 7 is a half sectional view showing a fourth preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through the axis O;
  • FIG. 5 is a half sectional view showing a second preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O;
  • FIG. 6 is a half sectional view showing a third preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O;
  • FIG. 7 is
  • FIG. 7 is a half sectional view showing a fifth preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O;
  • FIG. 10 is a half sectional view showing a sixth preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through the axis O;
  • FIG. 10 is a half sectional view showing a seventh preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through the axis O; It is a half sectional view which cuts and shows an example of the sealing device which concerns on a prior art by the plane which passes along the axis O.
  • FIG. 6 is a half sectional view showing another example of a sealing device according to the prior art by cutting along a plane passing through an axis O.
  • FIG. 1 is a cross-sectional view showing the first embodiment by cutting along a plane passing through the axis O.
  • reference numeral 100 is a wheel hub bearing, which is composed of an outer ring 101, an inner ring 102, and a number of steel balls 103 arranged so as to be able to roll between them.
  • the stationary side sealing element 1 attached to the inner periphery of the outer ring 101 and the rotary side sealing element 2 attached to the inner ring 102 are provided.
  • the outer ring 101 corresponds to the stationary member described in claim 1
  • the inner ring 102 corresponds to the rotating member described in claim 1.
  • the stationary-side sealing element 1 is made of a metal attachment ring 11 attached to the inner peripheral surface of the outer ring 101 and a rubber-like elastic material (rubber material or a synthetic resin material having rubber-like elasticity) attached to the attachment ring 11.
  • the first lip 12, the second lip 13, the third lip 14, and the fixed seal 15 are integrally formed.
  • the mounting ring 11 in the stationary-side sealing element 1 is manufactured by plastic working or the like of a metal plate, and has a cylindrical outer peripheral press-fit portion 11a that is press-fitted to the inner peripheral surface of the outer ring 101 of the bearing 100; It comprises a gasket support portion 11b formed with an appropriate small diameter at its outer end portion, and an inward flange 11c extending in the inner diameter direction from the inner end portion of the outer peripheral press-fit portion 11a.
  • the outer peripheral press-fitting portion 11 a has an outer diameter slightly larger than the inner peripheral surface of the outer ring 101 so that the outer peripheral press-fit portion 11 a is press-fitted into the inner peripheral surface of the outer ring 101 of the bearing 100 with an appropriate margin.
  • the first lip 12 in the stationary-side sealing element 1 has a cone whose tip has a large diameter from the base elastic layer 16 formed of a rubber-like elastic material on the outwardly facing surface of the inward flange 11c of the mounting ring 11.
  • the second lip 13 extends in a cylindrical shape, and is located on the inner peripheral side of the first lip 12, and has a conical cylindrical shape with a small diameter from the inner peripheral end of the base elastic layer 16.
  • the third lip 14 has a conical cylindrical shape with a tip having a small diameter from the inner peripheral end of the base elastic layer 16 toward the side opposite to the second lip 13 (inside the bearing).
  • the fixed seal 15 is formed in a mountain-shaped cross-sectional shape in which a part of the base elastic layer 16 wraps around the outer periphery of the gasket support portion 11 b in the attachment ring 11.
  • the rotation-side sealing element 2 is manufactured by plastic working of a metal plate or the like, and has a sleeve 21 fixed to the inner ring 102 that is a rotation member, and a seal flange 22 that expands in a disk shape from the outer end portion. .
  • a circumferentially continuous groove 102b is formed on the outer end surface 102a of the inner ring 102 of the bearing 100, and the sleeve 21 of the rotation-side sealing element 2 is press-fitted into a cylindrical surface 102c having an inner diameter of the groove 102b. ing.
  • the first lip 12 of the stationary-side sealing element 1 is slidably in close contact with the inner surface of the seal flange 22 of the rotating-side sealing element 2 (the surface facing the inner space B side of the bearing 100).
  • 13 and the third lip 14 are slidably in close contact with the outer peripheral surface of the inner ring 102 of the bearing 100, and the fixed seal 15 is in close contact with the inner peripheral surface of the outer ring 101 of the bearing 100 with an appropriate crushing allowance. .
  • the outer surface of the seal flange 22 (the surface facing the outside A side of the bearing 100) in the rotary side sealing element 2 is made of a rubber material or a synthetic resin material in which magnetic fine powders such as ferrite and rare earth are mixed throughout.
  • a multi-pole magnetized disk (pulsar ring) 3 which is formed in a disk shape and is alternately magnetized with N and S poles at a predetermined pitch in the circumferential direction is integrally provided.
  • This multi-pole magnetized disk 3 constitutes a magnetic encoder together with a magnetic sensor (not shown) arranged oppositely in a non-rotating state on the outside thereof.
  • the seal flange 22 and the multipolar magnetized disk 3 in the rotary side sealing element 2 have a gap between the outer diameter end and the rubber layer covering the inner peripheral surface of the gasket support portion 11b of the mounting ring 11 in the stationary side sealing element 1.
  • G1 is provided close to each other in the radial direction, and the inner surface of the seal flange 22 is between the closely sliding portions S1 and S2 of the first lip 12 and the second lip 13 and the fitting portion S3 of the sleeve 21. Is in close proximity to the end surface of the inner ring 102 of the bearing 100 (the end surface on the outer peripheral side of the groove 102b) 102a in the axial direction via the gap G2.
  • the intrusion of dust, muddy water or the like that has come from the outside A and passed through the gap G1 between the sealing flange 22 and the multipolar magnetized disk 3 and the stationary-side sealing element 1 is caused by the inner ring 102 of the bearing 100.
  • the seal flange 22 of the rotating side sealing element 2 that rotates integrally with the first lip 12 in the non-rotating stationary side sealing element 1 is blocked by the swinging action of the seal flange 22 due to centrifugal force. Even if dust, muddy water or the like may slightly pass from the intimate sliding portion S1 to the inner peripheral side thereof, these are in the intimate sliding portion S2 of the outer peripheral surface of the inner ring 102 and the second lip 13.
  • the third lip 14 prevents the grease from flowing out from the bearing internal space B.
  • fitting part S3 of the inner ring 102 of the bearing 100 and the sleeve 21 of the rotary side sealing element 2 is a fitting between metals, this fitting part S3 completely blocks the intrusion of muddy water or the like in the outside A. It is not a thing.
  • the multipolar magnetized disk 3 rotates integrally with the seal flange 22 of the rotary side sealing element 2, the N pole and S pole of the multipolar magnetized disk 3 are placed in front of the detection surface of the magnetic sensor (not shown). Passing alternately in the rotation direction, and a pulse-like signal having a waveform corresponding to the change in the magnetic field due to this is output from the magnetic sensor, so that the rotation can be measured by counting the pulses.
  • the multipolar magnetized disk 3 is provided with, for example, a top dead center of a piston for the purpose of controlling the ignition timing of the engine by providing a portion (not shown) having a different magnetization pitch at one place in the circumferential direction. It can also be the origin for detecting a specific position such as (TDC).
  • the fitting position of the sleeve 21 is rather than the outer peripheral surface of the inner ring
  • a plurality of magnetized tracks are formed on the outer diameter side and the inner diameter side of the multipolar magnetized disk 3 with the same phase interval and different phases from each other by an angle smaller than the phase interval.
  • FIG. 2 to FIG. 7 are one-side sectional views showing other preferred embodiments of the sealing device according to the present invention by cutting along a plane passing through the axis O.
  • the sleeve 21 of the rotary side sealing element 2 is press-fitted into the cylindrical surface 102d of the outer diameter of the groove 102b formed in the inner ring 102 of the bearing 100 in the circumferential direction. Only the point that it is fitted is different from the first embodiment described above, and an effect substantially similar to that of the first embodiment can be realized.
  • the inner surface of the seal flange 22 of the rotary side sealing element 2 is fitted to the sleeve 21 and the close sliding portions S1 and S2 of the first lip 12 and the second lip 13. Only the point which is in contact with the end surface (end surface on the outer peripheral side of the groove 102b) 102a of the inner ring 102 of the bearing 100 at a position between the portion S3 is different from the first embodiment described above. According to this configuration, even if muddy water, dust or the like of the outside A enters the groove 102b from the fitting portion S3 of the inner ring 102 and the sleeve 21, the contact portion S4 between the inner ring 102 and the seal flange 22 is provided on the outer peripheral side.
  • the 4th form shown by FIG. 4 is an outer diameter of the groove
  • the inner surface of the seal flange 22 of the rotary side sealing element 2 is in close contact with the first lip 12 and the second lip 13 as in the third embodiment.
  • the end surface of the inner ring 102 of the bearing 100 (the end surface on the outer peripheral side of the groove 102b) 102a is in contact.
  • Other portions are configured in the same manner as in the first embodiment.
  • the outer diameter portion 22a of the seal flange 22 in the rotary side sealing element 2 is replaced with the gasket support portion 11b (gasket support portion 11b) of the mounting ring 11 in the stationary side seal element 1.
  • the outer side of the end surface of the covering rubber layer) is extended to the outer diameter side, and the end surface of the gasket support portion 11b and the end surface 101a of the outer ring 101 of the bearing 100 are close to each other in the axial direction via gaps G3 and G4, thereby sealing.
  • a non-contact seal portion including gaps G3 and G4 is formed on the outer diameter side of the close sliding portion S1 between the flange 22 and the first lip 12.
  • Other portions are configured in the same manner as in the first embodiment.
  • the outer diameter portion 22a of the seal flange 22 extends to a position facing the end surface 101a of the outer ring 101 of the bearing 100 in the axial direction, gaps G3 and G4 that are long in the radial direction between the outer ring 101 and the outer ring 101. Since the non-contact seal portion is formed and the outer diameter portion 22a of the seal flange 22 is increased in diameter, not only the swinging action due to the centrifugal force is increased, but also a significant dynamic pressure is generated. Dust and muddy water are more difficult to enter.
  • the fitting position of the sleeve 21 is positioned on the inner diameter side with respect to the outer peripheral surface of the inner ring 102, the radial width of the seal flange 22 is expanded to the inner diameter side, and the outer diameter portion 22a of the seal flange 22 is expanded. Is extended to a position facing the end surface 101a of the outer ring 101 of the bearing 100 in the axial direction, so that the radial width of the seal flange 22 is expanded to the outer diameter side, so that the magnetized area of the multipolar magnetized disk 3 is increased. Can be further increased.
  • the sixth embodiment shown in FIG. 6 extends from the outer diameter end portion of the multipolar magnetized disk 3 in the axial direction to the outer diameter portion 22a of the seal flange 22 in the fifth embodiment described above.
  • a cylindrical portion 31 is provided which is close to (encloses) in the radial direction and surrounds the outer peripheral surface of the outer ring 101 via a narrow gap G5, whereby the outer diameter side of the close sliding portion S1 between the seal flange 22 and the first lip 12 is provided.
  • a non-contact seal portion composed of the gaps G3, G4 and G5 is formed. Other portions are configured in the same manner as in the first embodiment.
  • the cylindrical part 31 can also be shape
  • the seventh embodiment shown in FIG. 7 extends from the outer diameter portion 22a of the seal flange 22 in the fifth embodiment described above in the axial direction through the outer peripheral surface of the outer ring 101 of the bearing 100 and a narrow gap G5.
  • a cylindrical portion 23 that is closely opposed (enclosed) is formed, and thereby a non-contact seal portion including gaps G3, G4, and G5 is formed on the outer diameter side of the close sliding portion S1 between the seal flange 22 and the first lip 12. Formed.
  • Other portions are configured in the same manner as in the first embodiment.
  • the non-contact seal portion is extended to the outer peripheral side of the outer ring 101 of the bearing 100, dust and muddy water flying from the outside A further invades. Can be difficult to do.
  • the fitting portion S3 of the sleeve 21 of the rotation side sealing element 2 with respect to the inner ring 102 of the bearing 100 is configured in the same manner as in FIG.
  • the flange 22 and the end surface 102a of the inner ring 102 are in contact with each other in the same manner as in FIG. 3, it is needless to say that this may be configured in the same manner as in FIG.

Landscapes

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

Abstract

A sealing device that performs sealing by a throw off effect due to the rotation of a seal flange (22) of a rotating-side sealing element (2), wherein defects due to muddy water etc., which enters from a fitting section for the rotating-side sealing element (2) and a rotary member (102) to which the rotating-side sealing element (2) is attached, are prevented. The sealing device is thus provided with: a stationary-side sealing element (1) that is attached to a stationary member (101), and has a first lip (12) and a second lip (13); and the rotating-side sealing element (2), which has a sleeve (21) fitted to the rotary member (102) on the inner diameter side of the static member (101) and the seal flange (22) extending from the end of the sleeve (21) and in intimate slidable contact with the first lip (12). The second lip (13) is in intimate slidable contact with the rotary member (102), and the sleeve (21) is fitted to a cylindrical surface (102c) formed so as to be positioned on the rotary member (102) to the outer side from an intimate contact sliding section (S2) of the second lip (13) and on the inner diameter side.

Description

密封装置Sealing device
　本発明は、自動車や一般機械、産業機械等におけるベアリング等へダストや泥水が侵入するのを防止する密封装置において、回転側密封要素の振り切り作用によってシールを行うものに関する。 The present invention relates to a sealing device that prevents dust and muddy water from entering a bearing or the like in an automobile, a general machine, an industrial machine, etc., and performs sealing by swinging off a rotating side sealing element.
　自動車のベアリングを密封する密封装置の一種として、回転側密封要素を有するものがある。図８は、この種の密封装置の典型的な従来技術を、軸心Ｏを通る平面で切断して示す片側断面図であり、図９は、回転側密封要素に磁気エンコーダの多極着磁円盤を設けた密封装置の典型的な従来技術を、軸心Ｏを通る平面で切断して示す片側断面図である。 One type of sealing device for sealing automobile bearings has a rotary side sealing element. FIG. 8 is a one-side cross-sectional view showing a typical prior art of this type of sealing device cut along a plane passing through the axis O, and FIG. 9 is a multi-pole magnetization of a magnetic encoder on a rotary-side sealing element. 1 is a half sectional view showing a typical prior art of a sealing device provided with a disk by cutting along a plane passing through an axis O. FIG.
　図８又は図９に示される密封装置は、例えばベアリング１００の外輪１０１（静止側）の内周に装着される静止側密封要素１１０と、前記ベアリング１００の内輪（回転側）１０２の外周に嵌着されるスリーブ１２１及びその一端から延びるフランジ１２２からなる金属製の回転側密封要素１２０とを備え、静止側密封要素１１０に設けられたスラストリップ１１１が、回転側密封要素１２０のフランジ１２２に摺動可能に密接され、静止側密封要素１１０にスラストリップ１１１の内周側に位置して設けられたラジアルリップ１１２及びグリース用リップ１１３が、回転側密封要素１２０のスリーブ１２１の外周面に摺動可能に密接されている。 The sealing device shown in FIG. 8 or FIG. 9 is fitted to the outer periphery of the stationary ring sealing element 110 attached to the inner periphery of the outer ring 101 (stationary side) of the bearing 100 and the inner ring (rotation side) 102 of the bearing 100, for example. And a metal rotating side sealing element 120 comprising a flange 122 extending from one end of the sleeve 121 and a thrust strip 111 provided on the stationary side sealing element 110 slid on the flange 122 of the rotating side sealing element 120. A radial lip 112 and a grease lip 113 which are movably brought into close contact with each other and are provided on the inner side of the thrust strip 111 on the stationary side sealing element 110 slide on the outer peripheral surface of the sleeve 121 of the rotary side sealing element 120. Be as close as possible.
　また、図９に示される密封装置では、回転側密封要素１２０のフランジ１２２の外側面に、磁性体の微粉末を混合したゴム材料又は合成樹脂材料で円盤状に成形されると共に円周方向所定ピッチでＮ極とＳ極が交互に着磁された多極着磁円盤（パルサーリング）１３０が一体に設けられている。この多極着磁円盤１３０は、その外側に非回転状態で対向配置された不図示の磁気センサと共に磁気エンコーダを構成するものである。 Further, in the sealing device shown in FIG. 9, the outer surface of the flange 122 of the rotary side sealing element 120 is formed into a disk shape with a rubber material or a synthetic resin material mixed with fine powder of magnetic material and has a predetermined circumferential direction. A multi-pole magnetized disk (pulsar ring) 130 in which N poles and S poles are alternately magnetized at a pitch is integrally provided. This multi-pole magnetized disk 130 constitutes a magnetic encoder together with a magnetic sensor (not shown) arranged oppositely in a non-rotating state on the outside thereof.
　そして図８又は図９に示される密封装置は、回転側密封要素１２０のフランジ１２２とスラストリップ１１１の密接摺動部において、内輪１０２と一体的に回転するフランジ１２２の遠心力による振り切り作用によって、ベアリング１００の外部Ａからのダストや泥水等の侵入を阻止するものである。また、フランジ１２２とスラストリップ１１１の密接摺動部からその内周側へダストや泥水等が僅かに通過しても、これらは回転側密封要素１２０のスリーブ１２１とラジアルリップ１１２の密接摺動部においてシールされ、フランジ１２２の遠心力による振り切り作用によって、スラストリップ１１１の外周側へ押し戻される。また、図９に示される密封装置の場合は、このようなシール機能に加えて、多極着磁円盤１３０に対向配置された不図示の磁気センサが、その前面を回転によってＮ極とＳ極が交互に通過することによる磁界の変化に対応した波形のパルス信号を発生し、回転を検出するものである（例えば特許文献１，２参照）。 The sealing device shown in FIG. 8 or FIG. 9 has a swing-off action due to the centrifugal force of the flange 122 that rotates integrally with the inner ring 102 at the intimate sliding portion of the flange 122 of the rotating side sealing element 120 and the thrust strip 111. Intrusion of dust, muddy water, and the like from the outside A of the bearing 100 is prevented. Further, even if dust, muddy water or the like slightly passes from the intimate sliding portion of the flange 122 and the thrust strip 111 to the inner peripheral side thereof, the intimate sliding portion of the sleeve 121 and the radial lip 112 of the rotary side sealing element 120 And is pushed back to the outer peripheral side of the thrust strip 111 by the swing-off action by the centrifugal force of the flange 122. In addition, in the case of the sealing device shown in FIG. 9, in addition to such a sealing function, a magnetic sensor (not shown) disposed opposite to the multipolar magnetized disk 130 rotates the front surface thereof by rotating the front face with an N pole and an S pole. A pulse signal having a waveform corresponding to a change in the magnetic field due to the alternating passage of waves is generated, and rotation is detected (see, for example, Patent Documents 1 and 2).
特開平１１－８３５４３号公報Japanese Patent Laid-Open No. 11-83543 特開２００８－１６８６６５号公報JP 2008-168665 A
　しかしながら、上述した従来の技術によれば、回転側密封要素１２０のスリーブ１２１が、内輪１０２の外周面に金属同士で接触しているため、外部Ａの泥水などが、スリーブ１２１と内輪１０２との嵌合面間の微小隙間からベアリング１００の内部空間Ｂへ浸入するおそれがあった。 However, according to the above-described conventional technique, the sleeve 121 of the rotation-side sealing element 120 is in contact with the outer peripheral surface of the inner ring 102 with metals, so that muddy water or the like of the outer A is caused between the sleeve 121 and the inner ring 102. There was a risk of entering the internal space B of the bearing 100 from a minute gap between the fitting surfaces.
　本発明は、以上のような点に鑑みてなされたものであって、その技術的課題は、回転側密封要素のシールフランジの回転による振り切り作用によってシールを行う密封装置において、回転側密封要素とこの回転側密封要素が取り付けられる回転部材との嵌着部から侵入する泥水等による不具合を防止することにある。 The present invention has been made in view of the above points, and a technical problem thereof is a sealing device that performs sealing by swinging off by rotation of a seal flange of a rotating side sealing element. The object is to prevent inconvenience due to muddy water or the like entering from the fitting portion with the rotating member to which the rotating side sealing element is attached.
　上述した技術的課題を有効に解決するための手段として、請求項１の発明に係る密封装置は、静止部材に取り付けられ第一リップ及び第二リップを有する静止側密封要素と、前記静止部材の内径側の回転部材に嵌着されるスリーブ及びその端部から延びて前記第一リップと摺動可能に密接されるシールフランジを有する回転側密封要素を備え、前記第二リップが前記回転部材に摺動可能に密接され、前記スリーブが前記回転部材に前記第二リップとの密接摺動部より外側かつ内径側に位置して形成された筒状面に嵌着されたものである。 As a means for effectively solving the technical problem described above, a sealing device according to the invention of claim 1 includes a stationary side sealing element attached to a stationary member and having a first lip and a second lip, and the stationary member. A rotation-side sealing element having a sleeve fitted to the rotation member on the inner diameter side and a seal flange extending from an end thereof and slidably in contact with the first lip; and the second lip is attached to the rotation member The sleeve is fitted in a slidable manner, and the sleeve is fitted on a cylindrical surface formed on the rotating member so as to be located outside and on the inner diameter side of the close sliding portion with the second lip.
　また、請求項２の発明に係る密封装置は、請求項１に記載の構成において、シールフランジが、第一リップ及び第二リップの密接摺動部とスリーブの嵌着部の間で回転部材の端面と当接されるものである。 According to a second aspect of the present invention, there is provided the sealing device according to the first aspect, wherein the seal flange is provided between the close sliding portion of the first lip and the second lip and the fitting portion of the sleeve. It is in contact with the end face.
　また、請求項３の発明に係る密封装置は、請求項１又は２に記載の構成において、シールフランジの外径部と静止部材が近接対向した非接触シール部が形成されたものである。 Further, in the sealing device according to the invention of claim 3, in the configuration of claim 1 or 2, a non-contact seal portion is formed in which the outer diameter portion of the seal flange and the stationary member are closely opposed to each other.
　また、請求項４の発明に係る密封装置は、請求項１～３のいずれかに記載の構成において、シールフランジの外側面に、多極着磁円盤が一体に設けられたものである。 The sealing device according to a fourth aspect of the present invention is the structure according to any one of the first to third aspects, wherein a multi-pole magnetized disk is integrally provided on the outer surface of the seal flange.
　請求項１の発明に係る密封装置によれば、回転部材と回転側密封要素のスリーブの嵌着面から外部の流体等が侵入しても、この侵入流体は静止側密封要素の第二リップと回転部材との密接摺動部でそれより内部への侵入が阻止されると共に、回転側密封要素のシールフランジの回転による振り切り作用によって静止側密封要素の第一リップと前記シールフランジの密接摺動部の外側へ排出されるので、優れたシール効果を奏する。 According to the sealing device of the first aspect of the present invention, even if an external fluid or the like enters from the fitting surface of the sleeve of the rotating member and the rotating side sealing element, the intruding fluid is separated from the second lip of the stationary side sealing element. The intimate sliding portion with the rotating member prevents intrusion from the inside, and the first lip of the stationary side sealing element and the sealing flange closely slide with each other by the swinging action caused by the rotation of the sealing flange of the rotating side sealing element. Since it is discharged to the outside of the part, it has an excellent sealing effect.
　請求項２の発明に係る密封装置によれば、回転部材と回転側密封要素のスリーブの嵌着面から外部の流体等が侵入しても、この侵入流体はシールフランジと回転部材の端面との当接部でシールされ、静止側密封要素の第二リップと回転部材との密接摺動部へ到達しにくくなるので、請求項１による効果に加え、一層優れたシール効果を奏する。 According to the sealing device of the second aspect of the present invention, even if an external fluid or the like enters from the fitting surface of the sleeve of the rotating member and the rotating side sealing element, the intruding fluid is not formed between the seal flange and the end surface of the rotating member. Since it is sealed at the abutting portion, it becomes difficult to reach the intimate sliding portion between the second lip of the stationary side sealing element and the rotating member, so that in addition to the effect of the first aspect, a more excellent sealing effect is achieved.
　請求項３の発明に係る密封装置によれば、シールフランジの外径部と静止部材との間の非接触シール部によって、外部の流体等が静止側密封要素の第一リップと回転側密封要素のシールフランジの密接摺動部へ侵入しにくくなるので、請求項１又は２による効果に加え、一層優れたシール効果を奏する。 According to the sealing device of the third aspect of the invention, the non-contact seal portion between the outer diameter portion of the seal flange and the stationary member allows the external fluid or the like to flow between the first lip of the stationary side sealing element and the rotary side sealing element. Therefore, in addition to the effect of the first or second aspect, a further excellent sealing effect can be obtained.
　請求項４の発明に係る密封装置によれば、シールフランジの径方向幅が大きいので、その外側面に設けられた多極着磁円盤の着磁面積を大きくすることができ、請求項１～３による効果に加え、優れた回転検出精度を得ることができる。 According to the sealing device of the fourth aspect of the present invention, since the radial width of the seal flange is large, the magnetized area of the multipolar magnetized disk provided on the outer surface thereof can be increased. In addition to the effect of 3, excellent rotation detection accuracy can be obtained.
本発明に係る密封装置の好ましい第一の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。1 is a half sectional view showing a first preferred embodiment of a sealing device according to the present invention by cutting along a plane passing through an axis O. FIG. 本発明に係る密封装置の好ましい第二の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 5 is a half sectional view showing a second preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O; 本発明に係る密封装置の好ましい第三の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 6 is a half sectional view showing a third preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O; 本発明に係る密封装置の好ましい第四の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 7 is a half sectional view showing a fourth preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through the axis O; 本発明に係る密封装置の好ましい第五の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 7 is a half sectional view showing a fifth preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through an axis O; 本発明に係る密封装置の好ましい第六の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 10 is a half sectional view showing a sixth preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through the axis O; 本発明に係る密封装置の好ましい第七の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 10 is a half sectional view showing a seventh preferred embodiment of the sealing device according to the present invention by cutting along a plane passing through the axis O; 従来の技術に係る密封装置の一例を、軸心Ｏを通る平面で切断して示す片側断面図である。It is a half sectional view which cuts and shows an example of the sealing device which concerns on a prior art by the plane which passes along the axis O. 従来の技術に係る密封装置の他の例を、軸心Ｏを通る平面で切断して示す片側断面図である。FIG. 6 is a half sectional view showing another example of a sealing device according to the prior art by cutting along a plane passing through an axis O.
　以下、本発明に係る密封装置の好ましい実施の形態について、図面を参照しながら説明する。まず図１は、第一の形態を、軸心Ｏを通る平面で切断して示す断面図である。 Hereinafter, preferred embodiments of the sealing device according to the present invention will be described with reference to the drawings. First, FIG. 1 is a cross-sectional view showing the first embodiment by cutting along a plane passing through the axis O.
　図１において、参照符号１００は、車輪のハブ用ベアリングで、外輪１０１と、内輪１０２と、その間に転動可能に配置された多数の鋼球１０３からなり、このベアリング１００を密封する密封装置は、外輪１０１の内周に取り付けられる静止側密封要素１と、内輪１０２に取り付けられる回転側密封要素２を備える。なお、外輪１０１は請求項１に記載された静止部材に相当するものであり、内輪１０２は請求項１に記載された回転部材に相当するものである。 In FIG. 1, reference numeral 100 is a wheel hub bearing, which is composed of an outer ring 101, an inner ring 102, and a number of steel balls 103 arranged so as to be able to roll between them. The stationary side sealing element 1 attached to the inner periphery of the outer ring 101 and the rotary side sealing element 2 attached to the inner ring 102 are provided. The outer ring 101 corresponds to the stationary member described in claim 1, and the inner ring 102 corresponds to the rotating member described in claim 1.
　詳しくは、静止側密封要素１は、外輪１０１の内周面に取り付けられる金属製の取付環１１と、この取付環１１にゴム状弾性材料（ゴム材料又はゴム状弾性を有する合成樹脂材料）によって一体に成形された第一リップ１２、第二リップ１３、第三リップ１４及び固定シール１５を有する。 Specifically, the stationary-side sealing element 1 is made of a metal attachment ring 11 attached to the inner peripheral surface of the outer ring 101 and a rubber-like elastic material (rubber material or a synthetic resin material having rubber-like elasticity) attached to the attachment ring 11. The first lip 12, the second lip 13, the third lip 14, and the fixed seal 15 are integrally formed.
　静止側密封要素１における取付環１１は、金属板の塑性加工等により製作されたものであって、ベアリング１００の外輪１０１の内周面に圧入嵌着される円筒状の外周圧入部１１ａと、その外端部に適宜小径に絞って形成されたガスケット支持部１１ｂと、前記外周圧入部１１ａの内端部から内径方向へ延びる内向きフランジ１１ｃからなる。そして前記外周圧入部１１ａは、ベアリング１００の外輪１０１の内周面に適当な締め代をもって圧入されるように、外径が、外輪１０１の内周面より僅かに大径に形成されている。 The mounting ring 11 in the stationary-side sealing element 1 is manufactured by plastic working or the like of a metal plate, and has a cylindrical outer peripheral press-fit portion 11a that is press-fitted to the inner peripheral surface of the outer ring 101 of the bearing 100; It comprises a gasket support portion 11b formed with an appropriate small diameter at its outer end portion, and an inward flange 11c extending in the inner diameter direction from the inner end portion of the outer peripheral press-fit portion 11a. The outer peripheral press-fitting portion 11 a has an outer diameter slightly larger than the inner peripheral surface of the outer ring 101 so that the outer peripheral press-fit portion 11 a is press-fitted into the inner peripheral surface of the outer ring 101 of the bearing 100 with an appropriate margin.
　静止側密封要素１における第一リップ１２は、取付環１１の内向きフランジ１１ｃにおける外部を向いた面にゴム状弾性材料で形成された基部弾性層１６から、先端が大径となるような円錐筒状をなして延びており、第二リップ１３は、第一リップ１２の内周側に位置して、基部弾性層１６の内周端部から先端が小径となるような円錐筒状をなして延びており、第三リップ１４は、基部弾性層１６の内周端部から第二リップ１３と反対側（ベアリング内部側）へ向けて、先端が小径となるような円錐筒状をなして延びており、固定シール１５は、基部弾性層１６の一部が取付環１１におけるガスケット支持部１１ｂの外周へ廻り込んで山形の断面形状に形成されている。 The first lip 12 in the stationary-side sealing element 1 has a cone whose tip has a large diameter from the base elastic layer 16 formed of a rubber-like elastic material on the outwardly facing surface of the inward flange 11c of the mounting ring 11. The second lip 13 extends in a cylindrical shape, and is located on the inner peripheral side of the first lip 12, and has a conical cylindrical shape with a small diameter from the inner peripheral end of the base elastic layer 16. The third lip 14 has a conical cylindrical shape with a tip having a small diameter from the inner peripheral end of the base elastic layer 16 toward the side opposite to the second lip 13 (inside the bearing). The fixed seal 15 is formed in a mountain-shaped cross-sectional shape in which a part of the base elastic layer 16 wraps around the outer periphery of the gasket support portion 11 b in the attachment ring 11.
　回転側密封要素２は金属板の塑性加工等により製作されたものであって、回転部材である内輪１０２に固定されるスリーブ２１と、その外端部から円盤状に展開するシールフランジ２２を有する。ベアリング１００の内輪１０２の外側端面１０２ａには円周方向へ連続した溝１０２ｂが形成されており、回転側密封要素２のスリーブ２１は、この溝１０２ｂの内径の筒状面１０２ｃに圧入嵌着されている。 The rotation-side sealing element 2 is manufactured by plastic working of a metal plate or the like, and has a sleeve 21 fixed to the inner ring 102 that is a rotation member, and a seal flange 22 that expands in a disk shape from the outer end portion. . A circumferentially continuous groove 102b is formed on the outer end surface 102a of the inner ring 102 of the bearing 100, and the sleeve 21 of the rotation-side sealing element 2 is press-fitted into a cylindrical surface 102c having an inner diameter of the groove 102b. ing.
　そして、静止側密封要素１の第一リップ１２は、回転側密封要素２のシールフランジ２２の内側面（ベアリング１００の内部空間Ｂ側を向いた面）に摺動可能に密接され、第二リップ１３及び第三リップ１４は、ベアリング１００の内輪１０２の外周面に摺動可能に密接され、固定シール１５は、ベアリング１００の外輪１０１の内周面に適当なつぶし代をもって密接されるものである。 The first lip 12 of the stationary-side sealing element 1 is slidably in close contact with the inner surface of the seal flange 22 of the rotating-side sealing element 2 (the surface facing the inner space B side of the bearing 100). 13 and the third lip 14 are slidably in close contact with the outer peripheral surface of the inner ring 102 of the bearing 100, and the fixed seal 15 is in close contact with the inner peripheral surface of the outer ring 101 of the bearing 100 with an appropriate crushing allowance. .
　回転側密封要素２におけるシールフランジ２２の外側面（ベアリング１００の外部Ａ側を向いた面）には、その全域に、フェライトや希土類等の磁性体微粉末を混合したゴム材料又は合成樹脂材料で円盤状に成形されると共に円周方向所定ピッチでＮ極及びＳ極が交互に着磁された多極着磁円盤（パルサーリング）３が一体に設けられている。この多極着磁円盤３は、その外側に非回転状態で対向配置された不図示の磁気センサと共に磁気エンコーダを構成するものである。 The outer surface of the seal flange 22 (the surface facing the outside A side of the bearing 100) in the rotary side sealing element 2 is made of a rubber material or a synthetic resin material in which magnetic fine powders such as ferrite and rare earth are mixed throughout. A multi-pole magnetized disk (pulsar ring) 3 which is formed in a disk shape and is alternately magnetized with N and S poles at a predetermined pitch in the circumferential direction is integrally provided. This multi-pole magnetized disk 3 constitutes a magnetic encoder together with a magnetic sensor (not shown) arranged oppositely in a non-rotating state on the outside thereof.
　また、回転側密封要素２におけるシールフランジ２２及び多極着磁円盤３は、外径端部が、静止側密封要素１における取付環１１のガスケット支持部１１ｂの内周面を覆うゴム層と隙間Ｇ１を介して径方向に近接対向しており、前記シールフランジ２２の内側面は、第一リップ１２及び第二リップ１３の密接摺動部Ｓ１，Ｓ２とスリーブ２１の嵌着部Ｓ３との間の位置が、ベアリング１００の内輪１０２の端面（溝１０２ｂの外周側の端面）１０２ａと隙間Ｇ２を介して軸方向に近接対向している。 Further, the seal flange 22 and the multipolar magnetized disk 3 in the rotary side sealing element 2 have a gap between the outer diameter end and the rubber layer covering the inner peripheral surface of the gasket support portion 11b of the mounting ring 11 in the stationary side sealing element 1. G1 is provided close to each other in the radial direction, and the inner surface of the seal flange 22 is between the closely sliding portions S1 and S2 of the first lip 12 and the second lip 13 and the fitting portion S3 of the sleeve 21. Is in close proximity to the end surface of the inner ring 102 of the bearing 100 (the end surface on the outer peripheral side of the groove 102b) 102a in the axial direction via the gap G2.
　以上の構成によれば、外部Ａから飛来してシールフランジ２２及び多極着磁円盤３と静止側密封要素１との隙間Ｇ１を通過したダストや泥水等の侵入は、ベアリング１００の内輪１０２と一体回転する回転側密封要素２のシールフランジ２２と、非回転の静止側密封要素１における第一リップ１２との密接摺動部Ｓ１において、遠心力によるシールフランジ２２の振り切り作用によって阻止される。そして、ダストや泥水等が、前記密接摺動部Ｓ１からその内周側へ僅かに通過することがあっても、これらは前記内輪１０２の外周面と第二リップ１３の密接摺動部Ｓ２においてシールされるので、ベアリング内部空間Ｂへ侵入することはできず、結局、シールフランジ２２の回転による振り切り作用によって、第一リップ１２の密接摺動部Ｓ１の外側へ排出される。また、第三リップ１４は、ベアリング内部空間Ｂからのグリースの流出を防止するものである。 According to the above configuration, the intrusion of dust, muddy water or the like that has come from the outside A and passed through the gap G1 between the sealing flange 22 and the multipolar magnetized disk 3 and the stationary-side sealing element 1 is caused by the inner ring 102 of the bearing 100. The seal flange 22 of the rotating side sealing element 2 that rotates integrally with the first lip 12 in the non-rotating stationary side sealing element 1 is blocked by the swinging action of the seal flange 22 due to centrifugal force. Even if dust, muddy water or the like may slightly pass from the intimate sliding portion S1 to the inner peripheral side thereof, these are in the intimate sliding portion S2 of the outer peripheral surface of the inner ring 102 and the second lip 13. Since it is sealed, it cannot enter the bearing inner space B, and is eventually discharged to the outside of the intimate sliding portion S1 of the first lip 12 by the swinging action by the rotation of the seal flange 22. The third lip 14 prevents the grease from flowing out from the bearing internal space B.
　一方、ベアリング１００の内輪１０２と回転側密封要素２のスリーブ２１の嵌着部Ｓ３は、金属同士の嵌合であるため、この嵌着部Ｓ３は外部Ａの泥水等の侵入を完全に遮断するものではない。しかしながら上記構成によれば、内輪１０２とスリーブ２１の嵌着部Ｓ３から外部Ａの泥水やダスト等が侵入しても、スリーブ２１の外径側は狭い隙間Ｇ２によるラビリンスシールが形成されており、さらにその外周側には静止側密封要素１の第二リップ１３と前記内輪１０２との密接摺動部Ｓ２が存在するため、前記泥水やダスト等がベアリング内部空間Ｂへ侵入することはできず、シールフランジ２２の回転による振り切り作用によって第一リップ１２の密接摺動部Ｓ１の外側へ排出されるので、優れたシール効果を奏する。 On the other hand, since the fitting part S3 of the inner ring 102 of the bearing 100 and the sleeve 21 of the rotary side sealing element 2 is a fitting between metals, this fitting part S3 completely blocks the intrusion of muddy water or the like in the outside A. It is not a thing. However, according to the above configuration, even if muddy water or dust of the outside A enters from the fitting portion S3 of the inner ring 102 and the sleeve 21, a labyrinth seal with a narrow gap G2 is formed on the outer diameter side of the sleeve 21, Furthermore, since there is a close sliding portion S2 between the second lip 13 of the stationary side sealing element 1 and the inner ring 102 on the outer peripheral side, the muddy water, dust, etc. cannot enter the bearing inner space B, Since it is discharged to the outside of the intimately sliding portion S1 of the first lip 12 by the swing-off action caused by the rotation of the seal flange 22, an excellent sealing effect can be obtained.
　また、多極着磁円盤３が回転側密封要素２のシールフランジ２２と一体に回転するため、不図示の磁気センサの検出面の正面を、多極着磁円盤３のＮ極とＳ極が回転方向へ交互に通過することになり、これによる磁界の変化に対応した波形のパルス状の信号が前記磁気センサから出力されるので、このパルスのカウントによって、回転を計測することができる。なお、多極着磁円盤３は、その円周方向１箇所に、着磁ピッチの異なる部分（不図示）などを設けることによって、エンジンの点火時期制御等の目的で、例えばピストンの上死点（ＴＤＣ）等の特定のポジションを検出するための原点とすることもできる。 Further, since the multipolar magnetized disk 3 rotates integrally with the seal flange 22 of the rotary side sealing element 2, the N pole and S pole of the multipolar magnetized disk 3 are placed in front of the detection surface of the magnetic sensor (not shown). Passing alternately in the rotation direction, and a pulse-like signal having a waveform corresponding to the change in the magnetic field due to this is output from the magnetic sensor, so that the rotation can be measured by counting the pulses. The multipolar magnetized disk 3 is provided with, for example, a top dead center of a piston for the purpose of controlling the ignition timing of the engine by providing a portion (not shown) having a different magnetization pitch at one place in the circumferential direction. It can also be the origin for detecting a specific position such as (TDC).
　そして上記構成によれば、回転側密封要素２のスリーブ２１をベアリング１００の内輪１０２の外周面に嵌着する従来構造のものと比較すると、スリーブ２１の嵌着位置が内輪１０２の外周面よりも内径側へ位置する分、シールフランジ２２の径方向幅が大きくなるので、その外側面に設けられた多極着磁円盤３の径方向幅も大きくすることができ、その着磁面積を大きくすることができる。したがって、例えば多極着磁円盤３の外径側と内径側に、位相間隔が同じで、かつその位相間隔より小さな角度だけ互いに異なる位相をもって複数の着磁トラックを形成するといった、マルチトラック形式の着磁パターンとすることによって、回転数や回転角のほか、回転方向も検出可能としたり、回転検出精度を向上させたりすることができる。 And according to the said structure, compared with the thing of the conventional structure which fits the sleeve 21 of the rotation side sealing element 2 to the outer peripheral surface of the inner ring | wheel 102 of the bearing 100, the fitting position of the sleeve 21 is rather than the outer peripheral surface of the inner ring | wheel 102. Since the radial width of the seal flange 22 is increased by the amount positioned on the inner diameter side, the radial width of the multipolar magnetized disk 3 provided on the outer surface can be increased, and the magnetization area is increased. be able to. Therefore, for example, a plurality of magnetized tracks are formed on the outer diameter side and the inner diameter side of the multipolar magnetized disk 3 with the same phase interval and different phases from each other by an angle smaller than the phase interval. By using a magnetized pattern, it is possible to detect not only the rotation speed and rotation angle but also the rotation direction, and to improve the rotation detection accuracy.
　次に図２～図７は、本発明に係る密封装置の好ましい他の形態を、軸心Ｏを通る平面で切断して示す片側断面図である。 Next, FIG. 2 to FIG. 7 are one-side sectional views showing other preferred embodiments of the sealing device according to the present invention by cutting along a plane passing through the axis O.
　このうち図２に示される第二の形態は、回転側密封要素２のスリーブ２１が、ベアリング１００の内輪１０２に形成された円周方向へ連続した溝１０２ｂの外径の筒状面１０２ｄに圧入嵌着されるものである点のみが、上述した第一の形態と異なるものであり、第一の形態とほぼ同様の効果を実現することができる。 2, the sleeve 21 of the rotary side sealing element 2 is press-fitted into the cylindrical surface 102d of the outer diameter of the groove 102b formed in the inner ring 102 of the bearing 100 in the circumferential direction. Only the point that it is fitted is different from the first embodiment described above, and an effect substantially similar to that of the first embodiment can be realized.
　また、図３に示される第三の形態は、回転側密封要素２のシールフランジ２２の内側面が、第一リップ１２及び第二リップ１３の密接摺動部Ｓ１，Ｓ２とスリーブ２１の嵌着部Ｓ３との間の位置で、ベアリング１００の内輪１０２の端面（溝１０２ｂの外周側の端面）１０２ａと当接している点のみが、先に説明した第一の形態と異なる。この構成によれば、外部Ａの泥水やダスト等が内輪１０２とスリーブ２１の嵌着部Ｓ３から溝１０２ｂ内へ侵入しても、その外周側には内輪１０２とシールフランジ２２との接触部Ｓ４が形成されているので、図１のような隙間Ｇ２によるラビリンスシールに比較して、泥水やダストを一層確実に遮断することができる。しかも第一の形態と同様、さらにその外周側には静止側密封要素１の第二リップ１３と前記内輪１０２との密接摺動部Ｓ２が存在するため、前記泥水やダスト等がベアリング内部空間Ｂへ侵入することはできず、シールフランジ２２の回転による振り切り作用によって第一リップ１２の密接摺動部Ｓ１の外側へ排出される。 3, the inner surface of the seal flange 22 of the rotary side sealing element 2 is fitted to the sleeve 21 and the close sliding portions S1 and S2 of the first lip 12 and the second lip 13. Only the point which is in contact with the end surface (end surface on the outer peripheral side of the groove 102b) 102a of the inner ring 102 of the bearing 100 at a position between the portion S3 is different from the first embodiment described above. According to this configuration, even if muddy water, dust or the like of the outside A enters the groove 102b from the fitting portion S3 of the inner ring 102 and the sleeve 21, the contact portion S4 between the inner ring 102 and the seal flange 22 is provided on the outer peripheral side. Therefore, muddy water and dust can be more reliably blocked as compared with the labyrinth seal with the gap G2 as shown in FIG. In addition, as in the first embodiment, there is a close sliding portion S2 between the second lip 13 of the stationary side sealing element 1 and the inner ring 102 on the outer peripheral side thereof, so that the muddy water, dust, etc. are contained in the bearing inner space B. The first lip 12 is discharged to the outside of the close sliding portion S <b> 1 by the swing-off action caused by the rotation of the seal flange 22.
　また、図４に示される第四の形態は、第二の形態と同様、回転側密封要素２のスリーブ２１が、ベアリング１００の内輪１０２に形成された円周方向へ連続した溝１０２ｂの外径の筒状面１０２ｄに圧入嵌着されると共に、第三の形態と同様、回転側密封要素２のシールフランジ２２の内側面が、第一リップ１２及び第二リップ１３の密接摺動部Ｓ１，Ｓ２とスリーブ２１の嵌着部Ｓ３との間の位置で、ベアリング１００の内輪１０２の端面（溝１０２ｂの外周側の端面）１０２ａと当接しているものである。その他の部分は、第一の形態と同様に構成されている。 Moreover, the 4th form shown by FIG. 4 is an outer diameter of the groove | channel 102b in which the sleeve 21 of the rotation side sealing element 2 continued in the circumferential direction formed in the inner ring | wheel 102 of the bearing 100 similarly to a 2nd form. The inner surface of the seal flange 22 of the rotary side sealing element 2 is in close contact with the first lip 12 and the second lip 13 as in the third embodiment. At a position between S2 and the fitting portion S3 of the sleeve 21, the end surface of the inner ring 102 of the bearing 100 (the end surface on the outer peripheral side of the groove 102b) 102a is in contact. Other portions are configured in the same manner as in the first embodiment.
　次に、図５に示される第五の形態は、回転側密封要素２におけるシールフランジ２２の外径部２２ａが、静止側密封要素１における取付環１１のガスケット支持部１１ｂ（ガスケット支持部１１ｂを覆うゴム層）の端面の外側を外径側へ延び、このガスケット支持部１１ｂの端面及びベアリング１００の外輪１０１の端面１０１ａに、隙間Ｇ３，Ｇ４を介して軸方向に近接対向することによって、シールフランジ２２と第一リップ１２の密接摺動部Ｓ１の外径側に隙間Ｇ３，Ｇ４からなる非接触シール部を形成したものである。その他の部分は、第一の形態と同様に構成されている。 Next, in the fifth embodiment shown in FIG. 5, the outer diameter portion 22a of the seal flange 22 in the rotary side sealing element 2 is replaced with the gasket support portion 11b (gasket support portion 11b) of the mounting ring 11 in the stationary side seal element 1. The outer side of the end surface of the covering rubber layer) is extended to the outer diameter side, and the end surface of the gasket support portion 11b and the end surface 101a of the outer ring 101 of the bearing 100 are close to each other in the axial direction via gaps G3 and G4, thereby sealing. A non-contact seal portion including gaps G3 and G4 is formed on the outer diameter side of the close sliding portion S1 between the flange 22 and the first lip 12. Other portions are configured in the same manner as in the first embodiment.
　この形態によれば、シールフランジ２２の外径部２２ａがベアリング１００の外輪１０１の端面１０１ａと軸方向に対向する位置まで延びているため、外輪１０１との間に径方向に長い隙間Ｇ３，Ｇ４からなる非接触シール部が形成され、シールフランジ２２の外径部２２ａが大径になることによって遠心力による振り切り作用が増大するばかりでなく、顕著な動圧も発生するため、外部Ａから飛来するダストや泥水が一層侵入しにくいものとなる。 According to this embodiment, since the outer diameter portion 22a of the seal flange 22 extends to a position facing the end surface 101a of the outer ring 101 of the bearing 100 in the axial direction, gaps G3 and G4 that are long in the radial direction between the outer ring 101 and the outer ring 101. Since the non-contact seal portion is formed and the outer diameter portion 22a of the seal flange 22 is increased in diameter, not only the swinging action due to the centrifugal force is increased, but also a significant dynamic pressure is generated. Dust and muddy water are more difficult to enter.
　しかも、スリーブ２１の嵌着位置が内輪１０２の外周面よりも内径側へ位置することによって、シールフランジ２２の径方向幅が内径側へ拡張されるのに加え、シールフランジ２２の外径部２２ａがベアリング１００の外輪１０１の端面１０１ａと軸方向に対向する位置まで延びることによって、シールフランジ２２の径方向幅が外径側へも拡張されているので、多極着磁円盤３の着磁面積を一層増大させることができる。 Moreover, since the fitting position of the sleeve 21 is positioned on the inner diameter side with respect to the outer peripheral surface of the inner ring 102, the radial width of the seal flange 22 is expanded to the inner diameter side, and the outer diameter portion 22a of the seal flange 22 is expanded. Is extended to a position facing the end surface 101a of the outer ring 101 of the bearing 100 in the axial direction, so that the radial width of the seal flange 22 is expanded to the outer diameter side, so that the magnetized area of the multipolar magnetized disk 3 is increased. Can be further increased.
　さらに、図６に示される第六の形態は、上述した第五の形態におけるシールフランジ２２の外径部２２ａに、多極着磁円盤３の外径端部から軸方向へ延びてベアリング１００の外輪１０１の外周面と狭い隙間Ｇ５を介して径方向に近接対向する（包囲する）筒状部３１を設け、これによって、シールフランジ２２と第一リップ１２の密接摺動部Ｓ１の外径側に、隙間Ｇ３，Ｇ４及びＧ５からなる非接触シール部を形成したものである。その他の部分は、第一の形態と同様に構成されている。なお、筒状部３１は多極着磁円盤３とは独立したゴム材料又は合成樹脂材料で成形することもできる。 Further, the sixth embodiment shown in FIG. 6 extends from the outer diameter end portion of the multipolar magnetized disk 3 in the axial direction to the outer diameter portion 22a of the seal flange 22 in the fifth embodiment described above. A cylindrical portion 31 is provided which is close to (encloses) in the radial direction and surrounds the outer peripheral surface of the outer ring 101 via a narrow gap G5, whereby the outer diameter side of the close sliding portion S1 between the seal flange 22 and the first lip 12 is provided. In addition, a non-contact seal portion composed of the gaps G3, G4 and G5 is formed. Other portions are configured in the same manner as in the first embodiment. In addition, the cylindrical part 31 can also be shape | molded with the rubber material or synthetic resin material independent of the multipolar magnetized disk 3.
　また、図７に示される第七の形態は、上述した第五の形態におけるシールフランジ２２の外径部２２ａから、軸方向へ延びてベアリング１００の外輪１０１の外周面と狭い隙間Ｇ５を介して近接対向する（包囲する）筒状部２３を形成し、これによって、シールフランジ２２と第一リップ１２の密接摺動部Ｓ１の外径側に隙間Ｇ３，Ｇ４及びＧ５からなる非接触シール部を形成したものである。その他の部分は、第一の形態と同様に構成されている。 Further, the seventh embodiment shown in FIG. 7 extends from the outer diameter portion 22a of the seal flange 22 in the fifth embodiment described above in the axial direction through the outer peripheral surface of the outer ring 101 of the bearing 100 and a narrow gap G5. A cylindrical portion 23 that is closely opposed (enclosed) is formed, and thereby a non-contact seal portion including gaps G3, G4, and G5 is formed on the outer diameter side of the close sliding portion S1 between the seal flange 22 and the first lip 12. Formed. Other portions are configured in the same manner as in the first embodiment.
　第六及び第七の形態によれば、第五の形態による効果に加え、非接触シール部がベアリング１００の外輪１０１の外周側まで延長されるため、外部Ａから飛来するダストや泥水がさらに侵入しにくいものとすることができる。 According to the sixth and seventh embodiments, in addition to the effects of the fifth embodiment, since the non-contact seal portion is extended to the outer peripheral side of the outer ring 101 of the bearing 100, dust and muddy water flying from the outside A further invades. Can be difficult to do.
　なお、図５，図６，図７（第五～第七の形態）では、ベアリング１００の内輪１０２に対する回転側密封要素２のスリーブ２１の嵌着部Ｓ３を図１と同様に構成し、シールフランジ２２と内輪１０２の端面１０２ａを図３と同様に当接させた構成としたが、これは、図２あるいは図４と同様に構成しても良いことはもちろんである。 5, FIG. 6 and FIG. 7 (fifth to seventh embodiments), the fitting portion S3 of the sleeve 21 of the rotation side sealing element 2 with respect to the inner ring 102 of the bearing 100 is configured in the same manner as in FIG. Although the flange 22 and the end surface 102a of the inner ring 102 are in contact with each other in the same manner as in FIG. 3, it is needless to say that this may be configured in the same manner as in FIG.
　また、上述した各実施の形態では、回転側密封要素２のシールフランジ２２に多極着磁円盤３を一体に設けたものについて説明したが、多極着磁円盤３を設けないものについても同様に構成することができる。 Moreover, although each embodiment mentioned above demonstrated what provided the multipolar magnetized disk 3 integrally in the seal flange 22 of the rotation side sealing element 2, it is the same also about the thing which does not provide the multipole magnetized disk 3. Can be configured.
１　静止側密封要素
１１　取付環
１２　第一リップ
１３　第二リップ
１４　第三リップ
１５　固定シール
２　回転側密封要素
２１　スリーブ
２２　シールフランジ
２３，３１　筒状部
３　多極着磁円盤
１００　ベアリング
１０１　外輪（静止部材）
１０２　内輪（回転部材）
１０２ｃ，１０２ｄ　筒状面
Ａ　外部
Ｂ　内部空間
Ｇ１～Ｇ５　隙間
Ｓ１，Ｓ２　密接摺動部 DESCRIPTION OF SYMBOLS 1 Static side sealing element 11 Mounting ring 12 1st lip 13 2nd lip 14 3rd lip 15 Fixed seal 2 Rotation side sealing element 21 Sleeve 22 Seal flange 23, 31 Cylindrical part 3 Multipolar magnetized disk 100 Bearing 101 Outer ring ( Stationary member)
102 Inner ring (rotating member)
102c, 102d Cylindrical surface A External B Internal space G1-G5 Gap S1, S2 Close sliding portion

Claims (4)

  1. 　静止部材に取り付けられ第一リップ及び第二リップを有する静止側密封要素と、前記静止部材の内径側の回転部材に嵌着されるスリーブ及びその端部から延びて前記第一リップと摺動可能に密接されるシールフランジを有する回転側密封要素を備え、前記第二リップが前記回転部材に摺動可能に密接され、前記スリーブが前記回転部材に前記第二リップとの密接摺動部より外側かつ内径側に位置して形成された筒状面に嵌着されたことを特徴とする密封装置。 A stationary-side sealing element having a first lip and a second lip attached to a stationary member, a sleeve fitted to a rotating member on the inner diameter side of the stationary member, and extending from an end thereof, and slidable with the first lip A rotating side sealing element having a sealing flange closely contacted with the second lip, the second lip being slidably in contact with the rotating member, and the sleeve being outside the intimate sliding portion with the second lip. And the sealing device characterized by being fitted to the cylindrical surface formed in the inner diameter side.
  2. 　シールフランジが、第一リップ及び第二リップの密接摺動部とスリーブの嵌着部の間で回転部材の端面と当接されることを特徴とする請求項１に記載の密封装置。 2. The sealing device according to claim 1, wherein the seal flange is in contact with the end face of the rotating member between the close sliding portion of the first lip and the second lip and the fitting portion of the sleeve.
  3. 　シールフランジの外径部と静止部材が近接対向した非接触シール部が形成されたことを特徴とする請求項１又は２に記載の密封装置。 3. The sealing device according to claim 1 or 2, wherein a non-contact seal portion is formed in which the outer diameter portion of the seal flange and the stationary member are in close proximity to each other.
  4. 　シールフランジの外側面に、多極着磁円盤が一体に設けられたことを特徴とする請求項１～３のいずれかに記載の密封装置。 The sealing device according to any one of claims 1 to 3, wherein a multi-pole magnetized disk is integrally provided on an outer surface of the seal flange.
PCT/JP2011/058504 2010-11-12 2011-04-04 Sealing device WO2012063506A1 (en)

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JP2010-253842 2010-11-12

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WO2014006436A1 (en) * 2012-07-05 2014-01-09 Aktiebolaget Skf A bearing device, a sensor-bearing unit and an apparatus comprising at least one such bearing device
EP3070355A1 (en) * 2015-03-16 2016-09-21 Deere & Company Bearing assembly and external bearing seal
CN113939663A (en) * 2019-06-12 2022-01-14 Nok株式会社 Sealing device

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WO2014006436A1 (en) * 2012-07-05 2014-01-09 Aktiebolaget Skf A bearing device, a sensor-bearing unit and an apparatus comprising at least one such bearing device
CN104471264A (en) * 2012-07-05 2015-03-25 Skf公司 A bearing device, a sensor-bearing unit and an apparatus comprising at least one such bearing device
US9494196B2 (en) 2012-07-05 2016-11-15 Aktiebolaget Skf Bearing device, a sensor-bearing unit and an apparatus comprising at least one such bearing device
EP3070355A1 (en) * 2015-03-16 2016-09-21 Deere & Company Bearing assembly and external bearing seal
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CN113939663A (en) * 2019-06-12 2022-01-14 Nok株式会社 Sealing device
CN113939663B (en) * 2019-06-12 2024-02-13 Nok株式会社 Sealing device

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