WO2020090484A1 - Roulement à rouleaux doté de poulie - Google Patents

Roulement à rouleaux doté de poulie Download PDF

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Publication number
WO2020090484A1
WO2020090484A1 PCT/JP2019/040786 JP2019040786W WO2020090484A1 WO 2020090484 A1 WO2020090484 A1 WO 2020090484A1 JP 2019040786 W JP2019040786 W JP 2019040786W WO 2020090484 A1 WO2020090484 A1 WO 2020090484A1
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WO
WIPO (PCT)
Prior art keywords
slinger
axial lip
axial
lip
outer ring
Prior art date
Application number
PCT/JP2019/040786
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English (en)
Japanese (ja)
Inventor
櫻井　武仁
Original Assignee
Ntn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 Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2020090484A1 publication Critical patent/WO2020090484A1/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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—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

Definitions

  • the present invention relates to a rolling bearing with a pulley that can prevent foreign matter such as water, mud, and dust from entering the inside of a rolling bearing that rotatably supports a pulley.
  • Rolling bearings with pulleys are used, for example, to drive automotive engine peripheral accessories such as idler pulleys and tension pulleys.Because it is an assembly that is exposed to the outside, the inside of rolling bearings that rotatably support the pulleys is In addition, in order to prevent foreign matter such as water, mud, and dust from entering, a sealing device that covers the outer ring and the inner ring with an annular seal is provided.
  • the outer circumference of the seal is fixed to the outer ring, a seal lip is provided on the inner circumference of the seal, and this seal lip is brought into sliding contact with the inner ring to allow relative rotation of the inner ring and the outer ring.
  • the seal lip For rolling bearings with idler pulleys that are used at high speeds, the seal lip must be a light contact type with less interference to prevent heat generation in the sliding parts of the seal. Further, since the seal fixed to the outer ring that rotates at high speed also rotates at high speed, the seal lip is deformed by the centrifugal force of rotation, and the interference of the seal lip is further reduced, and the sealing performance is deteriorated.
  • the sealing between the outer ring and the inner ring is sufficient to seal against water and dust from the outside, and water and dust are prevented from entering the inside of the bearing from between the seal lip and the inner ring. Therefore, it is difficult to install a shield plate called a slinger on the outside of the seal to prevent water and dust from directly contacting the seal lip and to prevent water and dust from entering between the seal and slinger of the bearing. It is made to fly to the outside by the centrifugal force during rotation.
  • a side surface on the slinger 105 side of a seal body 110 having a seal lip 111 that slides in contact with a portion 105a parallel to the inner peripheral side axis of the slinger 105 is provided.
  • a ring-shaped axial lip 112 that expands outward in the axial direction is formed, and the axial lip 112 is brought into sliding contact with a portion 105b perpendicular to the axis of the slinger 105 to seal foreign matter such as water or dust.
  • a method has been proposed in which the path reaching the periphery of the lip 111 is closed to improve the waterproof and dustproof properties of the bearing and to improve the sealing performance of the bearing (Patent Document 1).
  • Patent Document 2 discloses a rolling bearing sealing device that prevents deterioration of sealing performance due to a gap between the axial lip 112 and the vertical portion 105b of the slinger 105 during high-speed rotation.
  • an axial lip 122 is formed on the side surface 121 of the rolling bearing seal 120 toward the slinger 130. Then, at the tip of the axial lip 122, a cone-shaped first sliding contact portion 123 that expands in diameter toward the outside of the bearing and is brought into contact with the slinger 130 when the rotation of the bearing is stopped, and faces the outside of the bearing. And a second slidable contact portion 124 having an inverted conical shape that is in non-contact with the slinger 130 when the bearing is in a rotation stopped state.
  • the second slidable contact portion 124 of the axial lip 122 is In the high speed rotation state, it is brought into contact with the convex portion 131 of the slinger 130 by the action of centrifugal force.
  • reference numeral 140 indicates the outer ring of the rolling bearing
  • reference numeral 150 indicates the inner ring of the rolling bearing.
  • the rolling bearing sealing device disclosed in Patent Document 2 has a second sliding contact with the slinger 130 even if the sealing property is deteriorated by the centrifugal force acting on the first sliding contact portion 123 at the time of high speed rotation and muddy water enters.
  • the portion 124 can prevent the infiltration of muddy water into the interior.
  • the second sliding contact portion 124 is not in contact with the slinger when the operation of the bearing is stopped, so that the first sliding contact portion 123, The muddy water that has entered the space surrounded by the 2 sliding contact portion 124 and the slinger 130 enters the inside of the bearing, which causes rusting, seizure, and other troubles in the bearing.
  • an object of the present invention is to prevent the intrusion of muddy water or the like into the inside of the rolling bearing while preventing the torque of the rolling bearing with a pulley from increasing.
  • the present invention has an outer ring raceway surface on an inner peripheral surface, an outer ring having a pulley mounted on an outer peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and the outer ring raceway surface.
  • a plurality of rolling elements that are rotatably arranged between the inner ring raceway surface, a seal member attached to both end portions of the inner peripheral surface of the outer ring, and located on the outer side in the axial direction of the seal member, A slinger attached to both ends of the outer peripheral surface of the inner ring, the seal member, a seal lip slidingly contacting the outer peripheral surface of the inner ring, and an axial lip slidingly contacting the side surface of the slinger facing the seal member.
  • the axial lip includes a first axial lip that expands outward in the axial direction and a second axial lip that decreases outward in the axial direction.
  • the allip and the second axial lip contact the slinger in a state where the rotation of the outer ring is stopped, and when the outer ring is rotating at a high speed, the first axial lip is deformed radially outward by a centrifugal force. Characterized by being in non-contact with the slinger.
  • the first axial lip By making the thickness of the first axial lip 0.2 to 1 times the thickness of the second axial lip, the first axial lip is easily deformed radially outward by centrifugal force.
  • angle ⁇ between the first axial lip and the seal member be specified in the range of 10 ° to 80 °.
  • the first axial lip and the second axial lip are in contact with the slinger in a state where the rotation of the outer ring is stopped, water, dust, etc. may be present between the seal member and the slinger. Is hard to enter. Then, during high speed operation, the first axial lip is deformed radially outward due to centrifugal force and does not come into contact with the slinger. However, even if muddy water enters between the first axial lip and the slinger, it does not contact the second axial lip. The contact of the slinger prevents further infiltration of muddy water.
  • the seal member since the seal member is rotating at a high speed, the muddy water attached to the seal member is blown outward in the radial direction by the centrifugal force and discharged to the outside of the bearing. At this time, even if the second axial lip is deformed by the centrifugal force and the pressing force against the slinger increases, the first axial lip is not in contact with the slinger, so that the torque increase is suppressed.
  • FIG. 2 is an enlarged vertical sectional view showing a rolling bearing portion of FIG. 1 in a state where the outer ring is rotating at a high speed.
  • FIG. 2 is an enlarged vertical sectional view showing a seal member and a slinger of FIG. 1.
  • It is a reference drawing which shows the case where the angle with respect to the seal member of a 1st axial lip is small. It is a reference drawing showing a case where the angle of the 1st axial lip to a seal member is large.
  • a rolling bearing with a pulley has a rolling bearing 1 and a pulley 2 rotatably supported by the rolling bearing 1.
  • the rolling bearing 1 has an outer ring raceway surface 3a on the inner circumferential surface, an outer ring 3 on which a pulley 2 is mounted on the outer circumferential surface, and an inner ring raceway surface 4a on the outer circumferential surface. 4, a plurality of rolling elements 5 rotatably arranged between the outer ring raceway surface 3a and the inner ring raceway surface 4a, and a cage 6 for holding the plurality of rolling elements 5 at predetermined intervals.
  • the embodiment shown in FIGS. 1 to 3 is a deep groove ball bearing that uses balls as the rolling elements 5, it may be a cylindrical roller bearing that uses cylindrical rollers as the rolling elements 5.
  • the direction along the central axis of the rolling bearing 1 is “axial direction”
  • the direction orthogonal to the central axis is “radial direction”
  • the arc around the central axis is The direction is called “circumferential direction”.
  • Both end openings of the bearing opening formed between the facing portions of the outer ring 3 and the inner ring 4 are located on the seal member 7 mounted on both end portions of the inner peripheral surface of the outer ring 3 and on the outer side in the axial direction of the seal member 7.
  • the inner ring 4 is sealed by the slinger 8 mounted on both ends of the outer peripheral surface of the inner ring 4.
  • the seal member 7 is an annular member in which the outer side of the bearing of a metal cored bar 9 is covered with a rubber covering portion 10.
  • a fixing portion 11 for attaching the seal member 7 to the outer ring 3 is formed. Then, the fixed portion 11 is mounted in the seal groove 12 provided on the inner diameter surface of the outer ring 3, and the seal member 7 is fixed to the inner diameter surface of the outer ring 3.
  • a seal lip 13 is formed on the inner peripheral edge of the seal member 7 inside the bearing, and the seal lip 13 elastically contacts the inner side wall 14a of the seal groove 14 formed at the end of the outer diameter surface of the inner ring 4. ing.
  • the seal lip 13 rotates at high speed while slidingly contacting the inner side wall 14 a of the seal groove 14. Therefore, the seal lip 13 is in light contact with the inner wall 14a.
  • a cylindrical land portion 15 is formed outside the seal groove 14 formed at the end of the outer diameter surface of the inner ring 4, and the slinger 8 is attached to the land portion 15.
  • This slinger 8 is an annular metal plate.
  • the slinger 8 is formed with a cylindrical portion 8a on the inner peripheral side, the inner peripheral end of which is bent into a cylindrical shape toward the inside of the rolling bearing 1.
  • the slinger 8 is fixed to the inner ring 4 by press-fitting the cylindrical portion 8 a into the land portion 15 on the outer diameter side of the inner ring 4.
  • the outer end of the cylindrical portion 8a of the slinger 8 is bent toward the outer diameter side to form a flange 8b that faces the side surface of the seal member 7 in the axial direction.
  • the flange 8b includes a vertical portion 8c that extends perpendicularly from the outer end of the cylindrical portion 8a to the outer side in the radial direction from the outer side in the radial direction, and an axial outer side and a radial outer side from the outer end of the vertical portion 8c. And an inclined portion 8d extending obliquely toward.
  • the covering portion 10 for covering the core metal 9 of the seal member 7 is formed in a flat surface at a portion facing the flange 8b of the slinger 8, and is formed at a substantially central portion in the radial direction of the flat surface toward the outer side in the axial direction.
  • a first axial lip 16a that expands in diameter and a second axial lip 16b that decreases in diameter axially outward are formed on the inner diameter side of the first axial lip 16a.
  • the first axial lip 16a extends from the axially outer end surface of the covering portion 10 slightly inward of the ball PCD toward the axially outer side and the radially outer side. The first axial lip 16a is in contact with the inclined portion 8d when the bearing is not rotating.
  • the second axial lip 16b extends inward in the axial direction and inward in the radial direction from a portion of the axially outer end surface of the covering portion 10 that axially faces the boundary portion between the vertical portion 8c and the inclined portion 8d. .. When the bearing is not rotating, the second axial lip 16b is in contact with the vertical portion 8c.
  • the first axial lip 16a and the second axial lip 16b contact the inclined portion 8d of the flange 8b of the slinger 8 in a state where the rotation of the outer ring 3 is stopped, and when the outer ring 3 rotates at a high speed,
  • the first axial lip 16a is formed so as to be radially outwardly deformed by centrifugal force so as not to come into contact with the flange 8b of the slinger 8. Then, the first axial lip 16a is deformed radially outward by centrifugal force when the outer ring 3 is rotating at a high speed, and is not in contact with the flange 8b of the slinger 8.
  • the flange 8b of the slinger 8 is formed such that the inner diameter side thereof is formed in a vertical surface perpendicular to the axis of the rolling bearing 1, the second axial lip 16b contacts the vertical surface, and the second axial lip 16b contacts the vertical surface.
  • the radially outer portion of the surface is formed as an inclined surface that spreads outward in the axial direction, and the outer diameter end of the first axial lip 16a contacts the inclined surface.
  • the angle ⁇ between the first axial lip 16a and the flat surface of the covering portion 10 of the seal member 7 is set to 10 ° to 80 °, preferably 40 ° to 60 °.
  • the contact portion between the first axial lip 16a and the inclined surface of the flange 8b of the slinger 8 is on the outer diameter side of the inclined surface of the flange 8b, as shown in FIG.
  • the slinger 8 and the outer ring 3 may interfere with each other.
  • the angle is larger than 60 °, the contact portion between the first axial lip 16a and the inclined surface of the flange 8b of the slinger 8 is on the inner diameter side of the inclined surface of the flange 8b, as shown in FIG.
  • the flange 8b of the slinger 8 has to be formed so as to spread outward in the axial direction, and the size in the axial direction increases.
  • the first axial lip 16a is in contact with the inclined surface of the flange 8b of the slinger 8 that is inclined outward in the radial direction, and during high speed rotation, the first axial lip 16a does not hit and smoothly.
  • the flange 8b is not in contact with the flange 8b. That is, during high speed operation, the first axial lip 16a is deformed radially outward by the centrifugal force and is not in contact with the flange 8b of the slinger 8.
  • the second axial lip 16b does not come into non-contact with the flange 8b of the slinger 8 even if it is deformed radially outward by the centrifugal force.
  • the thickness of the first axial lip 16a is smaller than that of the second axial lip 16b so that the first axial lip 16a can be easily deformed radially outward by centrifugal force. It is desirable to form it to 0.2 to 1 times the thickness.
  • the inner ring 4 of the rolling bearing 1 is non-rotatably supported by screwing a bolt 19 inserted therein into a screw hole 18 formed on the shaft end surface of the pulley shaft 17.
  • the bolt 19 is provided with a large-diameter shaft portion 19b at an end portion of a screw shaft 19a, a flange 19c at an end portion of the large-diameter shaft portion 19b, and an end surface of the flange 19c.
  • a head portion 19d is provided, the large-diameter shaft portion 19b is fitted to the inner ring 4 of the rolling bearing 1, and the screw shaft 19a is screwed into the screw hole 18 of the pulley shaft 17 to tighten the inner ring. 4 is clamped and fixed from both sides by the flange 19c and the shaft end surface of the pulley shaft 17.
  • the pulley 2 has a belt guide wheel 22 on its outer peripheral portion, an annular flange 23 is formed on the inner diameter surface of the belt guide wheel 22, and a boss portion 24 is provided on the inner diameter portion of the annular flange 23. Further, an inward flange 25 is provided at one end of the boss portion 24, and an outer surface of the inward flange 25 is a tapered surface 26.
  • the pulley 2 is made of resin and is integrally molded with the outer diameter surface of the outer ring 3. In order to prevent relative rotation between the outer ring 3 and the pulley 2, the outer diameter surface of the outer ring 3 is knurled. I am giving it. Further, the pulley 2 may be a metal molded product or a metal turned product.
  • Rolling bearing 2 Pulley 3: Outer ring 3a: Outer ring raceway surface 4: Inner ring 4a: Inner ring raceway surface 5: Rolling element 6: Retainer 7: Seal member 8: Slinger 13: Seal lip 16a: First axial lip 16b: 2nd axial lip 17: Pulley shaft

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

Abstract

La présente invention aborde le problème consistant à empêcher une augmentation du couple d'un roulement à rouleaux pourvu d'une poulie, et à empêcher l'infiltration d'eau boueuse, etc. dans le roulement à rouleaux. Le roulement à rouleaux pourvu d'une poulie est pourvu d'une bague d'étanchéité (8) qui est positionnée à l'extérieur dans la direction axiale d'un élément d'étanchéité (7) installé aux deux extrémités de la surface périphérique interne d'une bague externe (3) et qui est installé aux deux extrémités de la surface périphérique externe d'une bague interne (4), une lèvre d'étanchéité (13) qui vient en contact coulissant avec la surface périphérique externe de la bague interne (4), et une lèvre axiale qui vient en contact coulissant avec une surface latérale de la bague d'étanchéité (8) qui fait face à l'élément d'étanchéité (7), la lèvre axiale comprenant une première lèvre axiale (16a) qui s'étend en diamètre vers l'extérieur dans la direction axiale, et une seconde lèvre axiale (16b) qui se contracte en diamètre vers l'extérieur dans la direction axiale; les première et seconde lèvres axiales (16a, 16b) viennent en contact avec la bague d'étanchéité (8) dans un état dans lequel la rotation de la bague externe (3) est arrêtée; et dans un état dans lequel la bague externe (3) tourne à grande vitesse, la première lèvre axiale (16a) est déformée vers l'extérieur dans la direction radiale par une force centrifuge de telle sorte que la première lèvre axiale ne vient pas en contact avec la bague d'étanchéité (8).
PCT/JP2019/040786 2018-10-31 2019-10-17 Roulement à rouleaux doté de poulie WO2020090484A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-204802 2018-10-31
JP2018204802A JP2020070860A (ja) 2018-10-31 2018-10-31 プーリ付き転がり軸受

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WO2020090484A1 true WO2020090484A1 (fr) 2020-05-07

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PCT/JP2019/040786 WO2020090484A1 (fr) 2018-10-31 2019-10-17 Roulement à rouleaux doté de poulie

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WO (1) WO2020090484A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022244839A1 (fr) * 2021-05-20 2022-11-24 Nok株式会社 Dispositif d'étanchéité

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6165915A (ja) * 1984-09-07 1986-04-04 エスカーエフ　ゲーエムベーハー 転がり軸受のシール装置
JP2009216139A (ja) * 2008-03-07 2009-09-24 Jtekt Corp 軸受用密封装置
JP2010025251A (ja) * 2008-07-22 2010-02-04 Jtekt Corp 転がり軸受用密封装置
JP2015161366A (ja) * 2014-02-27 2015-09-07 日本精工株式会社 シール付き転がり軸受

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6165915A (ja) * 1984-09-07 1986-04-04 エスカーエフ　ゲーエムベーハー 転がり軸受のシール装置
JP2009216139A (ja) * 2008-03-07 2009-09-24 Jtekt Corp 軸受用密封装置
JP2010025251A (ja) * 2008-07-22 2010-02-04 Jtekt Corp 転がり軸受用密封装置
JP2015161366A (ja) * 2014-02-27 2015-09-07 日本精工株式会社 シール付き転がり軸受

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022244839A1 (fr) * 2021-05-20 2022-11-24 Nok株式会社 Dispositif d'étanchéité

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Publication number Publication date
JP2020070860A (ja) 2020-05-07

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