WO2016068005A1 - Palier de roulement - Google Patents

Palier de roulement Download PDF

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Publication number
WO2016068005A1
WO2016068005A1 PCT/JP2015/079794 JP2015079794W WO2016068005A1 WO 2016068005 A1 WO2016068005 A1 WO 2016068005A1 JP 2015079794 W JP2015079794 W JP 2015079794W WO 2016068005 A1 WO2016068005 A1 WO 2016068005A1
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WO
WIPO (PCT)
Prior art keywords
bearing
seal member
seal
rolling bearing
seal lip
Prior art date
Application number
PCT/JP2015/079794
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English (en)
Japanese (ja)
Inventor
英康 坪田
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 WO2016068005A1 publication Critical patent/WO2016068005A1/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
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7826—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of the opposing surface cooperating with the seal, e.g. a shoulder surface of a bearing ring
    • 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
    • F16C33/7856—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 with a single sealing lip
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement

Definitions

  • the present invention relates to a rolling bearing used for, for example, an automobile transmission.
  • Patent Document 1 A seal structure for preventing intrusion has been proposed (Patent Document 1).
  • the proposed seal structure is applied to a deep groove ball bearing, for example, as shown in FIG. 9A, and includes a seal member 5 including an annular cored bar 6 and an elastic member 7 integrally fixed to the cored bar 6.
  • the seal member 5 is fitted and fixed in a seal mounting groove 2 b provided on the inner peripheral surface of the outer ring 2, and the seal lip portion 9 on the distal end side is in radial contact with the outer peripheral surface of the inner ring 1.
  • the seal lip portion 9 is made of a high wear material, and the tip end portion thereof is a tapered projecting portion 12. As a result, the seal lip portion 9 and the inner ring 1 are in contact with each other before the operation, but when the bearing rotates after the operation starts, the protruding portion 12 of the seal lip portion 9 gradually wears, and the inner ring 1 and the seal lip portion 9, a minute clearance is generated in the entire circumference or a part in the circumferential direction, so that the seal torque is completely eliminated.
  • the rolling bearing described in Patent Document 1 has the following problems because the seal land, which is the portion of the outer peripheral surface of the inner ring 1 that is in contact with the seal lip 9, has a linear cross section. That is, at the time before the start of operation, as shown in the partial enlarged view of FIG. 9B, the so-called interference allowance ⁇ 1 where the tip of the protruding portion 12 of the seal lip portion 9 is located radially inward from the outer peripheral surface of the inner ring 1 is shown. It is in a state with. Therefore, actually, as shown in FIGS. 10A and 10B, the seal lip portion 9 faces the outside (right side in the figure) or the inside (left side in the figure) with respect to the bearing space. As a result, the protruding portion 12 of the seal member 9 is not effectively worn, and the seal lip portion 9 is not in contact with the inner ring 1 or until the contact pressure is light enough to be regarded as zero. There was variation.
  • the object of the present invention is to stabilize the time until the seal lip portion is appropriately worn, and after a fine clearance is formed between the seal lip portion and the bearing race, foreign matter enters the bearing space. It is an object of the present invention to provide a rolling bearing capable of effectively preventing the above.
  • a rolling bearing according to the present invention is a rolling bearing including an inner ring and an outer ring, a plurality of rolling elements interposed between the raceways of the inner ring and the outer ring, and a seal member that seals a bearing space formed between the inner ring and the outer ring.
  • the seal member includes a seal lip portion in which a base end of the seal member main body is fixed to one of the inner ring and the outer ring and a seal lip portion is in contact with the other race ring on a distal end side of the seal member main body.
  • the cross-sectional shape of the protruding portion which is the tip side portion of the seal lip portion, is a tapered shape that narrows as it reaches the tip, and the seal member is in a state in which the seal member is incorporated into the bearing.
  • a pressing force is applied to the other bearing ring, and the protruding portion of the seal lip portion is used by rotating the bearing so that the protruding portion is It is made of a high wear material that wears out of contact or is lightly contacted so that the contact pressure can be regarded as zero, and the protruding portion of the seal lip portion is fitted into the other race ring so as to contact the bottom surface.
  • An annular groove is provided.
  • the protruding portion of the seal lip portion is made of a high wear material, when the bearing is used in a rotating state, the tip end of the protruding portion is worn early, resulting in non-contact or light contact, resulting in low torque. . Although it becomes non-contact or light contact, the effect
  • an annular groove is provided on the other race ring so that the protruding portion of the seal lip part fits into the bottom surface, so that the seal lip part is guided by the annular groove and the seal member is mounted. And the posture of the rotating seal lip is stabilized. For this reason, the time required for wear of the seal lip portion is stabilized, leading to a reduction in time until the clearance is formed.
  • the annular groove on the other raceway ring unlike the conventional case where the tip end of the seal lip portion is brought into contact with the flat outer peripheral surface, it is generated between the tip end of the seal lip portion and the other raceway ring.
  • the gap becomes a labyrinth shape so as to form a passage that cannot go straight in the axial direction, and the function of preventing a foreign matter from entering as a labyrinth seal is enhanced, resulting in an improvement in bearing life.
  • the cross-sectional shape of the seal lip portion may be a V-shaped bent shape that is bent at a waist portion that is an intermediate portion in the radial direction so that a recess is formed on the outer surface with respect to the bearing space.
  • the portion on the tip side of the waist is the protruding portion. Since the intermediate portion in the radial direction of the seal lip portion has a bent V-shaped bent shape, the posture of the seal lip portion can be stably maintained even if the protrusion portion wears during the bearing operation, The pressing force (reaction force) on the raceway can be kept constant.
  • the seal lip portion bends at the waist, and the protruding portion which is the tip of the lip is pressed against the other bearing ring with a surface pressure that can be worn.
  • the bending of the waist tends to return to the state before assembly of the seal member so as to follow it, so that the wear of the protruding portion continuously proceeds.
  • the reaction force of the seal lip portion with respect to the other raceway approaches “zero”, the wear of the seal lip portion is completed, and an optimum labyrinth clearance is formed.
  • the axial width of the annular groove is preferably larger than the axial internal clearance of the bearing. Therefore, it can prevent that the protrusion part of a seal lip part remove
  • the bearing type of the rolling bearing to which the present invention is applied may be a deep groove ball bearing or a double row tapered roller bearing. In any bearing type, the above-mentioned action / effect can be obtained.
  • the rolling bearing may be used for an automobile transmission.
  • the optimum labyrinth clearance is formed by the operation of the bearing, foreign matter such as gear wear powder in the transmission can be prevented from entering the bearing. Further, since the sealing torque can be reduced, the fuel consumption of the automobile can be reduced.
  • the seal member may be provided with an adsorption preventing communication portion that communicates the bearing space and the external space outside the seal member so that the pressures in both spaces are the same.
  • the adsorption preventing communication portion When the adsorption preventing communication portion is provided, the pressure in the bearing space and the external space becomes the same, so that the phenomenon that the seal member sticks to the bearing can be suppressed.
  • the lubrication method may be oil lubrication.
  • Oil lubrication is suitable for bearings for automobile transmissions where oil lubrication is fundamental.
  • FIG. 6B is an enlarged cross-sectional view of a main part in the middle stage of using the bearing of FIG. 6A in a rotating state to wear the protruding portion of the seal lip part.
  • FIG. 6B is an enlarged cross-sectional view of a main part in a state where the labyrinth clearance is formed by completing the wear of the seal lip part in the rolling bearing of FIG. 6A.
  • the rolling bearing according to this embodiment is used, for example, in an automobile transmission.
  • a plurality of rolling elements 3 are interposed between raceway surfaces 1a and 2a of an inner ring and outer rings 1 and 2 that are raceways.
  • These inner rings, outer rings 1 and 2 and rolling elements 3 are made of, for example, high carbon chrome bearing steel such as SUJ2, martensitic stainless steel, or the like. However, it is not limited to these steels.
  • a cage 4 for holding the rolling elements 3 is provided, and both ends of an annular bearing space formed between the inner ring and the outer rings 1 and 2 are sealed with seal members 5 respectively. Grease is initially sealed in the bearing.
  • This rolling bearing is a deep groove ball bearing in which the rolling element 3 is a ball, and in this example, is an inner ring rotating type in which the inner ring 1 is a rotating ring and the outer ring 2 is a fixed ring. It is also possible to use an outer ring rotating type in which the inner ring 1 is a fixed ring and the outer ring 2 is a rotating wheel.
  • a seal mounting groove 2b for fitting and fixing the annular seal member 5 is formed on the inner peripheral surface of the outer ring 2.
  • an annular groove 1 b into which a protruding portion 12 of a seal lip portion 9 described later in the seal member 5 is fitted is formed on the outer peripheral surface of the inner ring 1.
  • the annular groove 1b is shaped like a mortar with a deep central portion in the axial direction.
  • the axial width C of the annular groove 1b is larger than the axial internal clearance of the bearing.
  • the seal member 5 includes an annular cored bar 6 and an elastic member 7 fixed to the cored bar 6 integrally.
  • a seal member main body 8 is constituted by most of the cored bar 6 and the elastic member 7, and a seal lip portion 9 is constituted by the remaining portion of the elastic member 7, in this example, the inner peripheral side portion of the elastic member 7.
  • the seal lip portion 9 is shaped to contact the inner ring 1 in the radial direction.
  • the elastic member 7 is provided so as to cover the entire core bar 6 except for the inner surface of the standing plate portion 6 b of the core bar 6.
  • the seal member 5 is formed, for example, by vulcanization molding of a rubber material, and a metal core 6 is bonded to the elastic member 7 at the time of vulcanization molding.
  • the cored bar 6 has a cylindrical part 6a, a standing plate part 6b, and an inclined part 6c sequentially from the outer diameter side.
  • the upright plate portion 6b is disposed substantially in parallel to the end face on the axially inner side from the end faces of the inner ring and the outer rings 1 and 2.
  • the cylindrical portion 6a is connected to the base end of the standing plate portion 6b, and the standing plate portion 6b and the cylindrical portion 6a form an L-shaped cross section.
  • the base end of the seal member 5 formed by the cylindrical portion 6 a and the outer peripheral portion 7 a (a part of the elastic member 7) provided on the outer peripheral surface of the cylindrical portion 6 a is the base end of the seal member main body 8.
  • the base end of the seal member main body 8 is fitted and fixed in the seal mounting groove 2 b of the outer ring 2.
  • the outer peripheral portion 7a is fixed to the seal mounting groove 2b in an elastically deformed state, thereby further improving the sealing performance between the outer ring 2 and the base end of the seal member main body 8.
  • An inclined portion 6c that is inclined inward in the axial direction toward the inner diameter side is connected to the tip of the upright plate portion 6b.
  • the outer peripheral portion 7 a of the seal member 5 has an adsorption preventing communication portion 15 that communicates the bearing space and the external space outside the seal member 5 in a state where the seal member 5 is incorporated in the bearing.
  • the adsorption preventing communication portion 15 has a crescent shape that opens to the outer peripheral surface of the sheet member 5, and is provided at one place in the circumferential direction of the outer peripheral surface.
  • the outer surface of the standing plate portion 6b in the metal core 6 is covered with a uniform thin-walled cover portion 7b, and the inner and outer surfaces of the inclined portion 6c are covered with cover portions 7c and 7d, respectively.
  • the inner diameter side tips of the cover portions 7 c and 7 d become the tip of the seal member main body 8.
  • a seal lip portion 9 that contacts the outer peripheral surface of the inner ring 1 is provided at the tip of the seal member main body 8.
  • the elastic member 7 has the outer peripheral portion 7 a, cover portions 7 b, 7 c, 7 d, and a seal lip portion 9. 2A and 2B, the tip of the seal lip portion 9 is shown to bite into the bottom of the annular groove 1b of the inner ring 1. However, in practice, the tip of the seal lip portion 9 is in a state where the seal is attached. The inner ring 1 is in contact with a tightening allowance.
  • the seal lip portion 9 has a lip base end portion 10, a waist portion 11, and a protruding portion 12 in order from the outer diameter side, and these 10, 11, 12 are integrally formed. Yes.
  • the lip base end portion 10 extends a predetermined distance from the inner peripheral edge of the inclined portion 6 c of the metal core 6 to the inner diameter side, and serves as a radial base end portion of the seal lip portion 9.
  • the lip base end portion 10 has a cross-sectional shape that becomes thinner from the middle in the radial direction toward the inner diameter side tip, that is, the waist portion 11.
  • the inner diameter side portions of the inner surface on the bearing space side and the outer surface on the opposite side of the lip base end portion 10 are each formed in a cross-sectional shape that is inclined so as to reach the inner side in the axial direction toward the distal end on the inner diameter side.
  • the waist 11 is an intermediate portion in the radial direction of the seal lip 9 and is located between the lip base end 10 and the protrusion 12.
  • the seal member 5 is incorporated in the bearing, that is, in a state in which the protruding portion 12 of the seal lip portion 9 is fitted in the annular groove 1b of the inner ring 1, the seal lip portion 9 escapes to the outer surface with respect to the bearing space.
  • a bent shape having a V-shaped cross section bent at the waist 11 is formed.
  • the relief recess 13 in this case is a recess that is formed not only on the outer surface of the waist 11, but also on the surface that combines the outer diameter side surface of the protruding portion 12 and the inner diameter side portion of the outer surface of the lip base end portion 10.
  • the cross section is a cross section obtained by cutting the seal member 5 along a plane including the bearing axis.
  • the cross-sectional shape of the waist 11 is such that the middle in the radial direction of the waist 11 is the thinnest and becomes thicker toward both ends.
  • the waist portion 11 has first to fourth waist portions 11a to 11d sequentially from the outer diameter side to the inner diameter side in order to form the escape recess 13.
  • the 1st waist part 11a comprises the cross-sectional shape which becomes thin in the outermost diameter side part of the radial direction in the waist part 11 toward the inner diameter side.
  • the inner surface of the first waist portion 11a on the bearing space side is connected flatly to the inner diameter side portion of the inner surface of the lip base end portion 10, and the outer surface of the first waist portion 11a is the outer surface of the lip base end portion 10. It is connected flatly to the inner diameter side portion.
  • the inclination angle of the outer surface of the first waist portion 11a with respect to the plane perpendicular to the bearing axis is larger than the inclination angle of the inner surface of the first waist portion 11a with respect to the same plane.
  • the second waist portion 11b connected to the first waist portion 11a has a cross-sectional shape that becomes slightly thinner toward the inner diameter side.
  • the inclination angle of the outer surface of the second waist portion 11b with respect to the plane is made smaller than the inclination angle of the outer surface of the first waist portion 11a.
  • the third and fourth waist portions 11c and 11d each have a cross-sectional shape that becomes thicker toward the inner diameter side.
  • the inner surface of the third waist portion 11c is connected flatly to the inner diameter side portion of the inner surface of the second waist portion 11b, and the outer surface of the third waist portion 11c with respect to the plane is axially outward as it goes toward the inner diameter side tip. It is formed in a cross-sectional shape that inclines so as to reach.
  • the inner surface of the fourth waist portion 11d is connected flatly to the inner surface of the third waist portion 11c, and the outer surface of the fourth waist portion 11d with respect to the plane is inclined so as to reach the outer side in the axial direction toward the tip on the inner diameter side.
  • the cross-sectional shape is formed.
  • the protrusion 12 that is the tip side of the waist 11 has a tapered shape that narrows from the middle in the radial direction to the tip.
  • the inner diameter side portion of the inner side surface 12a on the bearing space side of the protruding portion 12 is formed in a cross-sectional shape that is inclined so as to reach the outer side in the axial direction toward the distal end on the inner diameter side.
  • the inner diameter side portion is formed in a cross-sectional shape that is inclined so as to reach the inner side in the axial direction toward the inner diameter side tip.
  • the protruding portion 12 becomes a tapered shape with a triangular cross-section with the axial thickness becoming thinner from the middle in the radial direction, and the surface pressure that can wear the protruding portion 12 easily acts on the seal lip portion 9. It has become.
  • an axial protruding portion 12c that protrudes in the axial direction on the outer side of the bearing is provided.
  • the axial protrusion 12c is set so as not to contact the outer surface of the lip base end 10. The reason for not contacting will be described.
  • the pressing force applied to the portion where the tip of the lip is in contact with the inner ring 1 assumes only the elasticity of rubber. If the axial protruding portion 12c comes into contact with the outer surface of the lip base end portion 10, the rubber A load other than the elasticity is applied and the rotational resistance is increased.
  • the projecting portion 12 is made of a high-abrasion material that is lightly contacted so that the projecting portion 12 becomes worn and non-contact or the contact pressure can be regarded as zero by using the bearing in a rotating state.
  • the high wear material is provided only on the projecting portion 12 which is the tip side portion, but is not limited to this example.
  • the protruding portion 12 and the waist portion 11 may be made of a high wear material, or the entire seal lip portion 9 extending over the protruding portion 12, the waist portion 11 and the lip base end portion 10 may be made of a high wear material.
  • the high wear material is made of, for example, a high wear rubber material. As other materials constituting the high wear material, a resin material, a solid lubricant, a nonwoven fabric, mild steel, or the like may be applied.
  • the seal lip portion 9 has a bent shape with a V-shaped cross section
  • the tip of the protruding portion 12 of the seal lip portion 9 contacts the bottom surface of the annular groove 1b of the inner ring 1 as shown in FIG. 4A.
  • a reaction force against the inner ring 1, that is, a pressing force acts on the protruding portion 12.
  • the seal lip portion 9 is formed into a V-shaped bent shape that is bent at the waist portion 11 that is an intermediate portion in the radial direction so that the concave portion 13 is formed on the outer surface with respect to the bearing space.
  • the seal lip portion 9 becomes like a spring bent at the waist portion 11, and gives a pressing force F1 in a certain radial direction.
  • the protruding portion 12 is pressed against the bottom of the annular groove 1b of the inner ring 1 with a wearable surface pressure.
  • the protruding portion 12 of the seal lip portion 9 does not move even if the axial shakiness of the bearing occurs as shown in FIG. 4B. It does not come off from the annular groove 1b. For this reason, the seal lip portion 9 is always stably held in an appropriate posture. Further, even if there is a difference between the bearing internal pressure and the external pressure during rotation, the posture of the seal lip portion 9 is not easily affected. When the bearing is rotated while the posture of the seal lip portion 9 is stable in this way, the tip of the protruding portion 12 made of a high wear material of the seal lip portion 9 is always worn in substantially the same state.
  • the protruding portion 12 of the seal lip portion 9 is fitted into the annular groove 1b, and a labyrinth passage that cannot advance straight in the axial direction is formed between the protruding portion 12 and the bottom surface of the annular groove 1b.
  • the clearance ⁇ s is a labyrinth clearance.
  • the labyrinth clearance ⁇ s is not necessarily formed evenly over the entire circumference, and may be formed only in a part of the circumferential direction.
  • the protrusion 12 While the protrusion 12 is being worn, the protrusion 12 is always held in the annular groove 1b and the seal lip portion 9 is held in an appropriate posture, so that the wear is performed stably. In any rolling bearing, there is almost no variation in time until the seal lip portion 9 is appropriately worn. The time required for wear is, for example, several tens of minutes. Finally, as shown in FIG. 4D, the tip end surface of the protruding portion 12 of the seal lip portion 9 is worn until it becomes a smooth curved surface.
  • the protruding portion 12 of the seal lip portion 9 is made of a high wear material, the tip of the protruding portion 12 is worn early by using the bearing in a rotating state, and becomes non-contact or light contact. , Low torque. Although it becomes non-contact or light contact, the effect
  • the seal lip portion 9 is guided by the annular groove 1b, and the seal member The posture of the seal lip portion 9 after installation and during rotation is stabilized. Therefore, the time required for wear of the seal lip portion 9 is stabilized, and the time until the labyrinth clearance ⁇ s is formed is reduced.
  • the labyrinth clearance ⁇ s By forming the labyrinth clearance ⁇ s, the following effects can be obtained. (1) Seal torque is reduced. (2) The self-heating of the bearing is lower than the conventional product. (3) Since the self-heating of the bearing is reduced, it is possible to select an oil having a lower viscosity than that of conventionally used oil. (4) When this rolling bearing is incorporated in the transmission, the loss of the entire transmission can be reduced. (5) Because of the labyrinth clearance ⁇ s, it is possible to prevent foreign matter having a large particle size that affects the bearing life from entering the bearing.
  • the tip of the protruding portion 12 of the seal lip portion 9 can always be worn in substantially the same state.
  • the axial width C of the annular groove 1b is smaller than the axial internal clearance of the bearing as shown in FIG. 6A, the wear is not performed as follows. That is, when the axial shakiness of the bearing occurs as shown in FIG. 6B, the side surface of the protruding portion 12 hits the side wall of the annular groove 1b, and the side surface of the protruding portion 12 wears in a stepped manner as shown in FIG. 6C. To do.
  • the seal lip portion 9 is a waist portion 11 that is a radially intermediate portion so that a recess 13 is formed on the outer surface of the bearing space. Therefore, when the seal member 5 is assembled into the bearing, the seal lip portion 9 is elastically deformed along the assembling direction. For this reason, when the seal member 5 is incorporated in the bearing, the seal lip portion 9 easily escapes to the outside of the bearing, and the seal lip portion 9 does not reverse undesirably.
  • the outer ring side of the seal member 5, that is, the base end of the seal member main body 8 can be prevented from slipping against the outer ring seal groove 2b, and the wear of the seal lip portion 9 is inhibited. There is nothing.
  • the elastic member 7 covers the entire core bar 6 except for the inner surface of the standing plate portion 6 b of the core bar 6, a part of the elastic member 7 at the proximal end of the seal member main body 8 is used. Is fixed to the seal groove 2b of the outer ring 2 in an elastically deformed state. Thereby, the sealing performance of the outer ring
  • FIG. 7 shows a second embodiment in which the present invention is applied to a double-row tapered roller bearing.
  • the rolling bearing includes a pair of inner rings 21 having raceway surfaces 21a on the outer peripheral surface, an outer ring 22 having double-row raceway surfaces 22a facing the raceway surfaces 21a of the pair of inner rings 21, and the inner rings and And a double row rolling element 23 incorporated between the outer rings 21 and 22.
  • the rolling element 23 is a tapered roller, and is configured as a double row tapered roller bearing.
  • the double row tapered rollers which are the rolling elements 23 are arranged in a combination in the back and are held by the cage 24 for each row. Both ends of the bearing space between the inner ring 21 and the outer ring 22 are sealed by seal members 25 and 25, respectively.
  • the seal member 25 is formed of a high wear material at the protruding portion 32 of the seal lip portion 29 and is fitted into an annular groove 21 b formed on the outer peripheral surface of the inner ring 21. .
  • FIG. 8 is a schematic view showing an example in which the rolling bearing shown in FIGS. 1 to 5 is incorporated in a transmission of an automobile.
  • the figure is an example of an automatic transmission.
  • the outer rings of the rolling bearings BR1 and BR1 are fitted to both ends in the axial direction of the case 43, and both ends of the main shaft 44 are rotatably supported by the inner rings of the bearings BR1 and BR1, respectively.
  • a counter shaft 45 is provided in the case 43 in parallel with the main shaft 44.
  • the countershaft 45 has a gear portion that meshes with the gear portion of the main shaft 44 and is rotatably supported by the case 23 via a bearing.
  • oil lubrication with the lubricating oil stored in the case 43 is performed.
  • the rolling bearings BR1 and BR1 are incorporated in the transmission of an automobile in this way, foreign matter such as gear wear powder in the transmission can be reliably prevented from entering the bearing, and the seal lip portion Regardless of the tightening allowance, the torque can be reduced by sufficiently and reliably wearing the seal member. Since it is possible to reduce the seal torque, it is possible to save the fuel consumption of the automobile.
  • the rolling bearing according to any of the embodiments may be used in a continuously variable transmission or a manual transmission.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

L'invention porte sur un palier de roulement qui est pourvu d'un élément de joint d'étanchéité (5) pour sceller hermétiquement l'espace de palier formé entre une bague interne (1) et une bague externe (2). L'élément de joint d'étanchéité (5) présente un corps d'élément de joint d'étanchéité (8) ayant une extrémité de base fixée à la bague externe (2), et le corps d'élément de joint d'étanchéité (8) possède une lèvre de joint d'étanchéité (9) disposée sur le côté d'extrémité avant du corps d'élément de joint d'étanchéité (8) et en contact avec la bague interne (1). La forme de section transversale d'une partie de saillie (12), qui est la partie de côté d'extrémité avant de la lèvre de joint d'étanchéité (9), est effilée vers l'extrémité avant. La partie de saillie (12) est constituée par un matériau à usure élevée. Lorsque le palier tourne pendant que l'élément de joint d'étanchéité (5) est monté dans le palier, la partie de saillie (12) s'use et devient sans contact ou à faible contact avec la bague interne (1). La surface périphérique externe de la bague interne (1) est pourvue d'une rainure annulaire (1b) dans laquelle la partie de saillie (12) est ajustée de façon à être en contact avec la surface inférieure de la rainure annulaire (1b).
PCT/JP2015/079794 2014-10-31 2015-10-22 Palier de roulement WO2016068005A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014222276A JP2016089882A (ja) 2014-10-31 2014-10-31 転がり軸受
JP2014-222276 2014-10-31

Publications (1)

Publication Number Publication Date
WO2016068005A1 true WO2016068005A1 (fr) 2016-05-06

Family

ID=55857344

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/079794 WO2016068005A1 (fr) 2014-10-31 2015-10-22 Palier de roulement

Country Status (2)

Country Link
JP (1) JP2016089882A (fr)
WO (1) WO2016068005A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001056030A (ja) * 1999-08-13 2001-02-27 Nsk Ltd 転がり軸受
WO2010105662A1 (fr) * 2009-03-16 2010-09-23 Aktiebolaget Skf Joint d'étanchéité et palier à roulement comprenant un tel joint d'étanchéité
JP2012233548A (ja) * 2011-05-09 2012-11-29 Ntn Corp 転がり軸受
JP2014148991A (ja) * 2013-01-31 2014-08-21 Ntn Corp 転がり軸受

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001056030A (ja) * 1999-08-13 2001-02-27 Nsk Ltd 転がり軸受
WO2010105662A1 (fr) * 2009-03-16 2010-09-23 Aktiebolaget Skf Joint d'étanchéité et palier à roulement comprenant un tel joint d'étanchéité
JP2012233548A (ja) * 2011-05-09 2012-11-29 Ntn Corp 転がり軸受
JP2014148991A (ja) * 2013-01-31 2014-08-21 Ntn Corp 転がり軸受

Also Published As

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