WO2017065238A1 - Structure de joint d'étanchéité de palier pivotant - Google Patents

Structure de joint d'étanchéité de palier pivotant Download PDF

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Publication number
WO2017065238A1
WO2017065238A1 PCT/JP2016/080440 JP2016080440W WO2017065238A1 WO 2017065238 A1 WO2017065238 A1 WO 2017065238A1 JP 2016080440 W JP2016080440 W JP 2016080440W WO 2017065238 A1 WO2017065238 A1 WO 2017065238A1
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WO
WIPO (PCT)
Prior art keywords
seal
ring
slewing bearing
seal structure
inner ring
Prior art date
Application number
PCT/JP2016/080440
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English (en)
Japanese (ja)
Inventor
平松　研吾
Original Assignee
Ntn株式会社
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Filing date
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Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2017065238A1 publication Critical patent/WO2017065238A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F16C43/045—Mounting or replacing seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
    • F16J15/3236—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips with at least one lip for each surface, e.g. U-cup packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16J15/3268—Mounting of sealing rings
    • F16J15/3276—Mounting of sealing rings with additional static sealing between the sealing, or its casing or support, and the surface on which it is mounted
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors

Definitions

  • the present invention is, for example, a swivel used for a swivel part of various machines used in the vicinity of the outdoors or indoors, such as a swivel seat for a yaw and a blade of a wind power generator, a deck crane, a construction machine, and a lifting machine.
  • the present invention relates to a seal structure of a bearing and a slewing bearing.
  • FIG. 12 is a sectional view of a general slewing bearing.
  • the slewing bearing holds the inner ring 1, the outer ring 2, the plurality of rolling elements 3 interposed between the inner ring 1 and the outer ring 2, and the plurality of rolling elements 3 at equal intervals in the circumferential direction.
  • the cage 4 and the seal members 30A and 30B that hold the lubricating grease in the bearing space 8 are main components.
  • the seal members 30A and 30B are mounted by inserting a base 30a into a concave seal mounting groove 31 formed in one of the inner ring 1 and the outer ring 2 (the inner ring 1 in the illustrated example).
  • the seal lip portion 30b extending from the base portion 30a is in axial contact with the width of the other race ring (the outer ring 2 in the illustrated example) with a margin.
  • a contact portion between the seal lip portion 30b and the outer ring 2 may open due to an increase in pressure in the bearing space 8, and grease sealed in the bearing space 8 may leak.
  • Patent Documents 1 and 2 have been proposed.
  • the seal member is fixed to the seal mounting groove using an adhesive.
  • Japanese Patent Application Laid-Open No. H10-228561 changes the structure of the seal mounting groove to a specification that does not require an adhesive.
  • JP 2011-27235 A Japanese Patent No. 5606972
  • the adhesive used for fixing the seal member and the seal mounting groove is a silane-based adhesive having a relatively low adhesive strength, so that it is more effective at the time of seal replacement than when other adhesives are used. Excellent peeling workability. However, since it still requires an adhesive stripping operation, a large number of man-hours are required for seal replacement.
  • Fig. 13 shows the seal structure of the slewing bearing described in Patent Document 2.
  • the seal fixing portion 41 is pressed against the seal fixing side inclined portion 44 of the seal mounting groove 43 provided in the convex raceway ring 42, and at the seal lip portion.
  • a certain main lip 45 is pressed against the seal sliding side inclined portion 47 of the concave raceway ring 46.
  • the tightening force of the seal fixing portion 41 and the tightening force of the main lip 45 are antagonistic, but there is a concern that the seal fixing portion 41 may be displaced due to the balance of the forces being lost.
  • the object of the present invention is to prevent grease leakage due to reversal or lifting of the seal lip when the internal pressure of the bearing rises when grease is supplied, etc., and also prevents the seal member from falling off the seal mounting groove
  • Another object is to provide a seal structure for a slewing bearing.
  • the seal structure of the slewing bearing according to the present invention is a swing structure in which raceway grooves are formed on the circumferential surfaces of the inner ring and outer ring, which are raceway rings, facing each other, and a plurality of rolling elements are provided between the raceway grooves of the inner ring and outer ring.
  • a seal structure of a bearing comprising a seal member made of an elastic body that seals an axial end of a bearing space between the inner ring and the outer ring, and one of the inner ring and the outer ring has a bearing ring,
  • the opposing peripheral surface has a seal mounting groove, and the seal member protrudes from the base and contacts the axially opposite side portions of the seal mounting groove on the opposing peripheral surface of the one bearing ring.
  • An insertion portion that is inserted into the mounting groove in a holding state, and one or a plurality of seal lip portions that are provided integrally with the base portion and that contact the other raceway of the inner ring and the outer ring.
  • One of the seal lip portions includes a main lip that extends so as to be positioned inward in the axial direction toward the tip, and the tip is in contact with the opposing circumferential surface of the other race ring.
  • An annular protrusion that protrudes in the radial direction is provided on the end side of the opposed peripheral surface of the main lip on the opposite peripheral surface.
  • the seal member is attached to one of the bearing rings by inserting the insertion portion of the seal member into the seal mounting groove of one of the bearing rings.
  • the seal member is positioned by contacting the base portion with both axial side portions of the seal mounting groove, and the positional displacement of the seal member is prevented by holding the insertion portion in the seal mounting groove.
  • the main lip of the seal member attached in this way is in contact with the opposing circumferential surface of the other raceway ring, thereby preventing grease leakage from the bearing space and entry of foreign matter into the bearing space from the outside.
  • the main lip is pushed outward in the axial direction of the bearing space. Since the main lip is inclined so as to be located on the inner side in the axial direction of the bearing space as it goes toward the tip, the main lip is bent toward the other raceway by being pushed outward in the axial direction of the bearing space, and the tip is on the other side. Is strongly pressed against the slidable contact surface portion on the opposing circumferential surface of the raceway. If the internal pressure becomes too high, the main lip tries to reverse so that the tip of the main lip exceeds the slidable contact surface, but the annular lip provided on the end side of the slidable contact surface is The inversion is regulated as follows. For this reason, it is possible to prevent the main lip from being reversed and the seal member from dropping off from the seal mounting groove.
  • the seal member has an internal pressure receiving portion that is positioned on the inner side in the axial direction as approaching the opposed peripheral surface of the one raceway ring on an axial end surface facing the bearing space of the base portion. It may be.
  • the internal pressure receiving portion receives the internal pressure of the bearing space, the internal pressure receiving portion is pressed against the peripheral surface of the one bearing ring facing each other.
  • position of a sealing member can be hold
  • the tapered shape may be such that at least a part of the internal pressure receiving portion is positioned on the inner side in the axial direction as it approaches the opposing circumferential surface of the one raceway ring.
  • the tapered portion of the internal pressure receiving portion is strongly pressed against the opposing circumferential surface of one of the race rings, so that the seal member has an appropriate posture. Easy to hold.
  • the insertion portion of the seal member has an insertion portion main body whose axial dimension is smaller than the seal attachment groove when not inserted into the seal attachment groove, and on both sides in the axial direction from the insertion portion main body.
  • the fin body may have a thin shape that is accommodated in the seal mounting groove by being bent so as to overlap the insertion portion main body by elastic deformation.
  • the radial thickness of the fin-like body is preferably 0.8 mm or more and 1.5 mm or less.
  • the surface facing the distal end side in the radial direction of the fin-like body is an inclined surface that recedes from the distal end side as the distance from the insertion portion main body is increased so that the insertion portion can be easily inserted into the seal mounting groove.
  • the angle formed by the inclined surface and the cylindrical surface whose center line is in the axial direction is preferably 15 ° or more and 30 ° or less.
  • This slewing bearing is, for example, a bearing that supports a blade of a wind power generator so as to be rotatable about an axis substantially perpendicular to the main shaft axis with respect to the main shaft, or a nacelle of the wind power generator is supported so as to be rotatable with respect to a support base. Used as a bearing.
  • the slewing bearings are formed in two rows on the inner ring 1 and the outer ring 2 that are the race rings, and on the outer circumferential surface 1 a and the inner circumferential surface 2 a that are the circumferential surfaces of the inner ring 1 and the outer ring 2 that face each other.
  • a plurality of rolling elements 3 in each row interposed between the raceway grooves 1b and 2b.
  • the rolling element 3 is a ball.
  • the plurality of rolling elements 3 in each row are held in a state of being separated from each other in the circumferential direction by the cage 4.
  • the cage 4 is manufactured from, for example, an iron plate.
  • the cage 4 made of an iron plate is disposed between the inner ring 1 and the outer ring 2 and has a pocket in which the rolling element 3 enters.
  • a spacer may be used instead of the cage 4.
  • Each of the raceway grooves 1b, 2b of the inner ring 1 and the outer ring 2 is composed of two curved surfaces.
  • the two curved surfaces constituting each raceway groove 1b, 2b are Gothic arch-shaped circular arcs having a radius of curvature larger than that of the rolling element 3 and having different centers of curvature.
  • Each rolling element 3 comes into contact with the curved surfaces of the raceway groove 1b of the inner ring 1 and the raceway groove 2b of the outer ring 2 at the contact points, and contacts the four points. That is, this slewing bearing is configured as a four-point contact ball bearing.
  • the inner ring 1 is provided with a plurality of through holes 5 at regular intervals in the circumferential direction. These through holes 5 are used, for example, for connecting and fixing the inner ring 1 to a casing, blade, or the like of a nacelle described later.
  • the outer ring 2 is also provided with a plurality of through holes 6 at regular intervals in the circumferential direction. These through-holes 6 are used, for example, for connecting and fixing the outer ring 2 to a support base described later.
  • the through holes 5 and 6 of the inner and outer rings 1 and 2 are formed in parallel to the bearing axial direction.
  • the inner ring 1 and the outer ring 2 are different from each other in the position of the axial end, in this example by the step ⁇ .
  • the axial end of the inner ring 1 is positioned axially outside or above the axial end of the outer ring 2, and the lower end of the inner ring 1 is the axial end of the outer ring 2. It is located on the outside in the axial direction, that is, on the lower side than the end in the axial direction.
  • the upper and lower ends of the bearing space 8 between the inner ring 1 and the outer ring 2 are sealed by annular seal members 7A and 7B attached to the races whose axial ends are located outside in the axial direction.
  • the bearing space 8 is filled with grease.
  • a seal member may be provided only on the side where it is not desired to leak.
  • a seal member may be provided only at the blade side end of the bearing space 8.
  • seal structure by the seal members 7A and 7B will be described. Since the seal structure at the upper end and the seal structure at the lower end of the bearing space 8 are basically the same, the seal structure at the upper end will be described as a representative.
  • a seal mounting groove 10 for mounting the seal member 7A is provided near the upper end of the outer peripheral surface 1a of the inner ring 1.
  • the seal mounting groove 10 in the illustrated example is a groove having a substantially rectangular cross-sectional shape extending from the outer peripheral surface 1a to the inner diameter side (left side in the figure).
  • an annular protrusion 11 that protrudes toward the inner diameter side is provided at the upper end of the inner peripheral surface 2 a of the outer ring 2.
  • the cross-sectional shape of the annular protrusion 11 in the illustrated example is a trapezoid whose protruding end edge is the upper base.
  • the seal member 7A is made of an elastic body such as nitrile or acrylic, and has a base 12 that is positioned in contact with the outer peripheral surface 1a of the inner ring 1, and protrudes from the base 12 to the inner diameter side and is inserted into the seal mounting groove 10.
  • the insertion portion 13 is provided with a main lip 14 and a sub lip 15 which are provided integrally with the base portion 12 and have a distal end contacting the outer ring 2 as a seal lip portion.
  • the base 12 serves as a positioning reference for the seal member 7A, and extends from the main body portion 12a extending in the axial direction (vertical direction in the drawing) and the axially outer portion (upper portion in the drawing) of the main body portion 12a.
  • the insertion part 13 protrudes from the axial center part of the main body part 12a to the inner diameter side.
  • the inner peripheral surface 12aa of the main body portion 12 a is in contact with both axial portions of the seal mounting groove 10 on the outer peripheral surface 1 a of the inner ring 1.
  • the inner pressure receiving portion 12c is provided on the inner end surface in the axial direction of the main body portion 12a, that is, on the end surface facing the bearing space 8, closer to the outer peripheral surface 1a of the inner ring 1.
  • the internal pressure receiving portion 12c in this example is provided in a portion close to the outer peripheral surface 1a of the inner ring 1 on the end surface facing the bearing space 8, and is tapered toward the inner side in the axial direction as the outer peripheral surface 1a of the inner ring 1 is approached. It is.
  • a portion of the internal pressure receiving portion 12c that is in contact with the outer peripheral surface 1a of the inner ring 1 is formed with a chamfer having an arc cross section.
  • the insertion portion 13 includes an insertion portion main body 13a and a plurality of rows (in this example, two rows) of fin-like bodies 13b formed on both axial sides of the insertion portion main body 13a.
  • the fin-like body 13b has a thin shape that can be bent so as to overlap the insertion portion main body 13a by elastic deformation.
  • the axial dimension A1 of the insertion portion main body 13a is smaller than the axial dimension B of the seal mounting groove 10.
  • the fin-like body 13b is in an upright posture in the axial direction.
  • the axial dimension A2 between the tips of the two fin-like bodies 13 on both axial sides of the insertion portion main body 13a is larger than the axial dimension B of the seal mounting groove 10.
  • the insertion portion 13 When the insertion portion 13 is pushed into the seal attachment groove 10, the fin-like body 13 is pushed against the wall surface of the seal attachment groove 10, and the axial dimension is reduced. Thereby, as shown in FIG. 2, the insertion portion 13 can be inserted into the seal attachment groove 10.
  • the fin-like body 13 b In a state where the insertion portion 13 is inserted into the seal attachment groove 10, the fin-like body 13 b is pressed against the wall surface of the seal attachment groove 10 by its own elastic restoring force, and this causes the insertion portion 13 to come out of the seal attachment groove 10. Resistance. For this reason, even if an external force is applied to the seal member 7 ⁇ / b> A, the seal member 7 ⁇ / b> A is not easily dropped from the seal mounting groove 10.
  • the thickness t in the radial direction of the fin-like body 13b is preferably 0.8 mm or more and 1.5 mm or less.
  • the surface facing the inner diameter side which is the distal end side in the radial direction of the fin-like body 13b, recedes from the distal end side as the distance from the insertion portion main body 13a increases so that the insertion portion 13 can be easily inserted into the seal mounting groove 10.
  • the inclined surfaces are 13ba and 13bb.
  • the angle ⁇ formed by the tapered surfaces 13ba, 13bb and the cylindrical surface (the distal end surface of the insertion portion 13 in the example shown in the figure) whose axial direction is the center line direction is preferably 15 ° or more and 30 ° or less. .
  • the main lip 14 extends in an inclined manner so as to be positioned on the inner side in the axial direction from the inner end in the axial direction of the base body 12a toward the tip in the state before the seal member 7A shown in FIG. 3A is attached.
  • the main lip 14 In the attached state of the seal member 7 ⁇ / b> A shown in FIG. 2, the main lip 14 is curved inward in the axial direction, and the tip thereof comes into contact with the sliding contact surface portion 2 aa on the inner peripheral surface 2 a of the outer ring 2.
  • the annular protrusion 11 is located on the end side with respect to the sliding contact surface portion 2aa.
  • the auxiliary lip 15 is inclined so as to be positioned on the inner side in the axial direction from the protruding portion 12b of the base portion 12 toward the tip in the state before the seal member 7A shown in FIG. In the attached state of the seal member 7 ⁇ / b> A shown in FIG. 2, the sub lip 15 is bent outward in the axial direction as a whole, and the tip thereof contacts the width surface 2 c of the outer ring 2.
  • the seal member 7 ⁇ / b> A is placed in a posture in which the main lip 14 faces downward, and the main lip 14 is positioned above the bearing space 8.
  • the shape of the seal member 7A or the like so that the maximum radial direction distance SP from the main lip 14 to the internal pressure receiving portion 12c in the above posture does not exceed the distance BA between the outer peripheral surface 1a of the inner ring 1 and the annular protrusion 11 of the outer ring 2.
  • the dimensions of each part are determined. In FIG. 4, the deformation of the main lip 14 and the sub lip 15 is ignored and illustrated.
  • the main lip 14 enters the bearing space 8 as in step (B) by lowering the seal member 7A downward while maintaining the above posture.
  • the insertion portion 13 is brought close to the seal attachment groove 10 while changing the posture of the seal member 7A as in step (C).
  • the insertion portion 13 is inserted into the seal attachment groove 10 by pushing the seal member 7A toward the inner diameter side as in step (D). Thereby, the attachment of the seal member 7A is completed.
  • the seal member 7A is attached to the inner ring 1 by inserting the insertion portion 13 of the seal member 7A into the seal attachment groove 10 of the inner ring 1 as shown in FIG.
  • the seal member 7A is positioned when the base portion 12 is in contact with both axial portions of the seal mounting groove 10, and the displacement of the seal member 7A is displaced when the insertion portion 13 is held in the seal mounting groove 10. Is prevented.
  • the main lip 14 of the seal member 7A attached in this way is in contact with the inner peripheral surface 2a of the outer ring 2, and the sub lip 15 is in contact with the width surface 2c of the outer ring 2, thereby causing grease leakage from the bearing space 8 and bearing from the outside. Intrusion of foreign matter into the space 8 is prevented.
  • the main lip 14 When the internal pressure of the bearing space 8 is increased during grease supply, the main lip 14 is pushed outward in the axial direction of the bearing space 8. Since the main lip 14 is inclined so as to be positioned on the inner side in the axial direction of the bearing space 8 toward the tip, the main lip 14 bends toward the outer ring 2 by being pushed outward in the axial direction of the bearing space 8, and the tip is The outer ring 2 is strongly pressed against the sliding contact surface portion 2aa on the inner peripheral surface 2a. If the internal pressure becomes too high, the tip of the main lip 14 tries to reverse beyond the slidable contact surface 2aa, but the annular protrusion 11 provided on the end side of the slidable contact surface 2aa The inversion as described above is regulated. For this reason, it is possible to prevent the main lip 14 from being inverted and the seal member 7A from falling off the seal mounting groove 10 accordingly.
  • the internal pressure receiving portion 12c is provided on the base portion 12 of the seal member 7A, the reversal of the main lip 14 is more effectively controlled. That is, when the internal pressure of the bearing space 8 rises, pressure is applied to the seal member 7A as shown by an arrow in FIG. 5A. Among these, the pressure within the range indicated by reference numeral 20 acts to float the base 12 from the outer peripheral surface 1 a of the inner ring 1, but the pressure within the range indicated by reference numeral 21 presses the base 12 against the outer peripheral surface 1 a of the inner ring 1. Acts as follows.
  • the internal pressure receiving portion 12c when the internal pressure receiving portion 12c has a tapered shape that is positioned on the inner side in the axial direction as it approaches the outer peripheral surface 1a of the inner ring 1, the internal pressure receiving portion 12c receives the internal pressure of the bearing space 8.
  • the internal pressure receiving portion 12c is strongly pressed against the outer peripheral surface 1a of the inner ring 1, and the seal member 7A is easily held in an appropriate posture. Since the main lip 14 is pressed against the sliding contact surface portion 2aa of the outer ring 2 by the pressure within the range indicated by reference numeral 20, the sealing performance between the main lip 14 and the sliding contact surface portion 2aa is not impaired.
  • the above analysis revealed the following.
  • the main lip 14 is deformed as the internal pressure increases.
  • the main lip 14 is not reversed because the annular lip 11 provided on the outer ring 2 restrains the deformation of the main lip 14 beyond a certain level.
  • the seal member 7A ′ of the comparative example is estimated to drop off around 0.5 MPa because a force acts in the direction of pulling out the insertion portion 13 from the seal mounting groove 10 due to internal pressure.
  • the seal member 7A of the embodiment presses the internal pressure receiving portion 12c against the inner ring 1, so that even if the internal pressure increases, there is almost no change in the posture of the seal member 7A, and the seal is sealed even if the internal pressure becomes high.
  • the member 7A can be prevented from falling off.
  • the seal structure of this embodiment includes the annular protrusion 11 provided on the outer ring 2, the internal pressure receiving portion 12c provided on the base 12 of the seal member 7A, and the fin provided on the insertion portion 13 of the seal member 7A.
  • the state-like body 13b can prevent grease leakage due to the reversal of the main lip 14 and the lifting from the sliding surface portion 2aa of the outer ring 2.
  • the internal pressure receiving portion 12c of the seal member 7A of the above embodiment has a tapered shape in which a part thereof is positioned on the inner side in the axial direction as it approaches the outer peripheral surface 1a of the inner ring 1, but is not limited to this shape.
  • a substantially entire region of the internal pressure receiving portion 12 c may have a tapered shape that is positioned on the inner side in the axial direction as it approaches the outer peripheral surface 1 a of the inner ring 1.
  • a part of the inner ring 1 in contact with the outer peripheral surface 1 a may have a step shape protruding inward in the axial direction.
  • the internal pressure receiving portion 12 c may have a spherical shape that is concave with respect to the bearing space 8 in the attached state of the seal member 7 ⁇ / b> A.
  • the seal member 7A is attached to the inner ring 1. The effect of pressing strongly against the outer peripheral surface 1a of is obtained.
  • the seal mounting groove 10 for mounting the seal member 7A is provided in the inner ring 1, and the main lip 14 and the sub lip 15 which are seal lip portions of the seal member 7A are in contact with the outer ring 2.
  • the inner ring 1 is one of the bearing rings referred to in the claims
  • the outer ring 2 is the other bearing ring referred to in the claims.
  • the seal attachment groove 10 for attaching the seal member 7B is provided in the outer ring 2, and the main lip 14 and the sub lip 15 of the seal member 7B are in contact with the inner ring 1.
  • the outer ring 2 is one of the bearing rings referred to in the claims
  • the inner ring 1 is the other bearing ring referred to in the claims.
  • One of the race rings may be either the inner ring 1 or the outer ring 2
  • the other race ring may be either the outer ring 2 or the inner ring 1.
  • seal members 7A and 7B of the above embodiments have the main lip 14 and the sub lip 15 as the seal lip portion, but the seal lip portion may be only the main lip 14, and the main lip 14 and the sub lip 15 You may have another seal lip part other than.
  • FIGS. 10 and 11 show an example of a wind power generator.
  • This wind power generator 51 is provided with a nacelle 53 on a support base 52 so as to be able to turn horizontally, and a main shaft 55 is rotatably supported in a casing 54 of the nacelle 53, and at one end of the main shaft 55 protruding outside the casing 54.
  • the blade 56 which is a swirl wing is attached.
  • the other end of the main shaft 55 is connected to a speed increaser 57, and the output shaft 58 of the speed increaser 57 is coupled to the rotor shaft of the generator 59.
  • the nacelle 53 is turnably supported by the turn bearing BR1.
  • a slewing bearing BR1 for the nacelle 53 having a gear or the like provided on the outer peripheral surface of the outer ring 2 is used.
  • a plurality of drive sources 60 are installed in the casing 54, and pinion gears are fixed to the drive sources 60 via reduction gears (not shown). It arrange
  • the outer ring 2 is connected and fixed to the support base 52 through the plurality of through holes 5, and the inner ring 1 (FIG. 1) is fixed to the casing 54.
  • the plurality of drive sources 60 are driven in synchronization, and this turning driving force is transmitted to the outer ring 2. Therefore, the nacelle 53 can turn relative to the support base 52.
  • the blade 56 is rotatably supported by the slewing bearing BR2.
  • This slewing bearing BR2 is a slewing bearing to which any one of the seal structures of the above-described embodiments is applied.
  • a bearing provided with a gear on the inner circumferential surface of the inner ring 1 is applied.
  • a driving source for rotating the blade 56 is provided at the protruding end portion 55 a of the main shaft 55.
  • the outer ring 2 of the slewing bearing is connected and fixed to the distal end portion 55a, and a gear provided on the inner peripheral surface of the inner ring 1 meshes with the pinion gear of the drive shaft. By driving this drive source and transmitting this turning drive force to the inner ring 1, the blade 56 can turn.
  • the slewing bearing BR2 supports the blade 56 of the wind power generator with respect to the main shaft 55 so as to be rotatable about an axis L2 substantially perpendicular to the main shaft axis L1. In this way, the angle of the blade 56 and the direction of the nacelle 53 are changed at any time according to the wind state.
  • the slewing bearing of the present invention can be applied to, for example, construction machines such as hydraulic excavators and cranes, rotary tables of machine tools, gun seats, parabolic antennas and the like in addition to wind power generators.

Landscapes

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

Abstract

L'invention concerne une structure de joint d'étanchéité d'un palier pivotant, laquelle structure comprend un élément de joint d'étanchéité (7A) formé à partir d'un corps élastique et scellant une partie d'extrémité axiale d'un espace de palier (8) entre une bague interne (1) et une bague externe (2). La bague interne (1) a une surface périphérique externe (1a) avec une rainure d'attachement de joint d'étanchéité (10). L'élément de joint d'étanchéité (7A) comprend : une partie de base (12) en contact avec les deux sections de côté axial de la rainure d'attachement de joint d'étanchéité (10) dans la surface périphérique externe (1a) de la bague interne (1) ; une partie d'insertion (13) faisant saillie à partir de la partie de base (12), et insérée et maintenue dans la rainure d'attachement de joint d'étanchéité (10) ; et une lèvre principale (14) disposée d'un seul tenant avec la partie de base (12), et ayant une extrémité de pointe en contact avec la bague externe (2). Une protubérance annulaire faisant saillie radialement (11) est disposée davantage vers un côté de partie d'extrémité qu'une partie de surface de contact de coulissement (2aa) d'une surface périphérique interne (2a) de la bague externe (2), la partie de surface de contact de coulissement (2aa) étant en contact avec l'extrémité de pointe de la lèvre principale (14).
PCT/JP2016/080440 2015-10-16 2016-10-13 Structure de joint d'étanchéité de palier pivotant WO2017065238A1 (fr)

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JP2015204613A JP2017075673A (ja) 2015-10-16 2015-10-16 旋回軸受のシール構造
JP2015-204613 2015-10-16

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110864046A (zh) * 2019-12-27 2020-03-06 瓦房店轴承集团国家轴承工程技术研究中心有限公司 爪式轴承密封结构
CN111894992A (zh) * 2020-08-06 2020-11-06 中国铁建重工集团股份有限公司 一种工程机械、主轴承和密封件
EP4276322A1 (fr) * 2022-05-12 2023-11-15 thyssenkrupp rothe Erde Germany GmbH Palier à roulement de grande dimension
WO2023217982A1 (fr) 2022-05-12 2023-11-16 thyssenkrupp rothe erde Germany GmbH Grand roulement
DE202023106612U1 (de) 2023-11-10 2023-12-12 Meteor GmbH Dichtung für eine Windkraftanlage

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114135585A (zh) * 2021-12-09 2022-03-04 中国铁建重工集团股份有限公司 一种掘进机主轴承及密封结构
CN114483772B (zh) * 2022-01-25 2023-10-31 中国铁建重工集团股份有限公司 一种具有高承载能力的回转支承

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10309383A1 (de) * 2002-03-04 2003-09-18 Imo Ind Momentenlager Stoll & Drehlagerung für der Feuchtigkeit ausgesetzte Anlagen
JP2012193826A (ja) * 2011-03-18 2012-10-11 Ntn Corp 旋回軸受のシール構造および旋回軸受
JP2014009752A (ja) * 2012-06-29 2014-01-20 Nok Corp オイルシール

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10309383A1 (de) * 2002-03-04 2003-09-18 Imo Ind Momentenlager Stoll & Drehlagerung für der Feuchtigkeit ausgesetzte Anlagen
JP2012193826A (ja) * 2011-03-18 2012-10-11 Ntn Corp 旋回軸受のシール構造および旋回軸受
JP2014009752A (ja) * 2012-06-29 2014-01-20 Nok Corp オイルシール

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110864046A (zh) * 2019-12-27 2020-03-06 瓦房店轴承集团国家轴承工程技术研究中心有限公司 爪式轴承密封结构
CN111894992A (zh) * 2020-08-06 2020-11-06 中国铁建重工集团股份有限公司 一种工程机械、主轴承和密封件
EP4276322A1 (fr) * 2022-05-12 2023-11-15 thyssenkrupp rothe Erde Germany GmbH Palier à roulement de grande dimension
WO2023217982A1 (fr) 2022-05-12 2023-11-16 thyssenkrupp rothe erde Germany GmbH Grand roulement
DE202023106612U1 (de) 2023-11-10 2023-12-12 Meteor GmbH Dichtung für eine Windkraftanlage

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