WO2016204220A1 - Palier à rouleaux effilés et dispositif de palier planétaire - Google Patents

Palier à rouleaux effilés et dispositif de palier planétaire Download PDF

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Publication number
WO2016204220A1
WO2016204220A1 PCT/JP2016/067919 JP2016067919W WO2016204220A1 WO 2016204220 A1 WO2016204220 A1 WO 2016204220A1 JP 2016067919 W JP2016067919 W JP 2016067919W WO 2016204220 A1 WO2016204220 A1 WO 2016204220A1
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WO
WIPO (PCT)
Prior art keywords
outer ring
tapered roller
annular portion
cage
bearing
Prior art date
Application number
PCT/JP2016/067919
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English (en)
Japanese (ja)
Inventor
将太 若山
貴行 鈴木
Original Assignee
Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2016204220A1 publication Critical patent/WO2016204220A1/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
    • F16C19/22—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
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating

Definitions

  • the present invention relates to a tapered roller bearing disposed between a planetary rotating body and a carrier shaft provided in a planetary reduction gear, and a planetary bearing device using the tapered roller bearing, and more particularly to a terminal provided in a drive system of a very large dump truck.
  • the present invention relates to a device suitable for a reduction gear.
  • final reduction gears are arranged inside the wheel rim.
  • This final reduction gear generally has a structure in which planetary reduction gears are combined in a plurality of stages, and the output from the final stage planetary reduction gears is transmitted to the wheel rim.
  • the planetary rotating body and the rolling bearing provided in each planetary reduction gear are lubricated by lubricating oil stored in an oil bath in the housing of the final reduction gear (for example, Patent Document 1 below).
  • a pair of tapered roller bearings is arranged between the planetary rotating body and the carrier shaft of the planetary reduction gear.
  • the planetary rotator revolves while rotating, and the tapered roller bearing and the carrier shaft revolve integrally with the planetary rotator.
  • the lower part in the housing of the final reduction gear is an oil bath.
  • the lubricating oil for the oil bath enters the inside of the revolving planetary rotor and flows into the tapered roller bearing (for example, Patent Document 2 below).
  • centrifugal force due to the tapered roller bearing revolving integrally with the planetary rotating body also acts on the lubricating oil inside the cage and the bearing.
  • Centrifugal force caused by the revolution of the planetary rotor causes a load region in the tapered roller bearing, and causes deformation and eccentricity of the cage and bias of the lubricating oil inside the bearing.
  • the inventors of the present application examined the usage environment in the final reduction device of the current ultra-large dump truck, and the revolution diameter of the tapered roller bearing was about 500 mm, the revolution speed exceeded 500 rpm, and the bearing rotation speed became about 1300 rpm.
  • the maximum centrifugal acceleration was about 75G.
  • strong centrifugal acceleration acts in this manner, the lubricating oil inside the bearing becomes lean in the load region, and the tendency to deviate toward the opposite side in the circumferential direction from the load region becomes significant.
  • the column part is strongly pressed against the tapered roller due to deformation of the cage due to centrifugal acceleration or the like in a load region where the lubrication conditions are bad, abnormal wear may occur in the column part and the cage may be destroyed at an early stage.
  • the problem to be solved by the present invention is to prevent abnormal wear of the pillar portion of the cage in the tapered roller bearing disposed between the planetary rotating body of the planetary reduction gear and the shaft of the carrier. is there.
  • the present invention provides a tapered roller bearing disposed between a planetary rotating body and a carrier shaft provided in a planetary reduction gear, wherein the outer ring, the inner ring, and the cone interposed between the outer ring and the inner ring.
  • the cage since the cage is guided in the radial direction by the inner circumference of the outer ring, it is not necessary to set the clearance between the column portion and the tapered roller as narrow as in the rolling element guide system. Moreover, since the large-diameter second annular portion has the flange, the rigidity of the cage can be improved. For this reason, even when the cage is deformed by the action of centrifugal force, it is possible to prevent strong contact between the column portion and the tapered roller. Further, since the flange protrudes toward the inner ring side, it plays a role of pulling up the lubricating oil flowing into the bearing inside the bearing, and can be expected to promote the inflow of lubricating oil into the bearing.
  • the outer circumference of the cage and the position of the inner circumference are arranged close to the outer ring side, and between the inner circumference of the cage and the inner ring. It is possible to widen the gap. For this reason, it is possible to make it easier for the lubricating oil to flow into the bearing through the inner circumference of the cage and the inner ring.
  • the lubricating oil flowing between the inner periphery of the cage and the inner ring travels toward the outer ring through the clearance between the pocket column and the tapered roller by the action of centrifugal force. For this reason, it is possible to make the lubricant easily reach the guided surface of the column part or the cage.
  • the strong contact between the retainer column and the tapered roller due to the centrifugal force is prevented by adopting the above configuration. Since the flowability of the lubricating oil into the bearing is improved and the flowing lubricating oil easily reaches the guided surface of the column portion and the cage, abnormal wear of the column portion can be prevented.
  • Sectional drawing which shows the lower part side of the planetary bearing apparatus which concerns on 1st Embodiment of this invention.
  • Front view showing a second annular portion of a cage according to a second embodiment of the present invention.
  • the partial front view of the 2nd annular part of the cage concerning a 3rd embodiment of this invention
  • Sectional drawing which shows the tapered roller bearing which concerns on 3rd Embodiment Partial top view of the cage according to the fourth embodiment of the present invention
  • FIG. 1 shows a cross section on the lower side of the first embodiment.
  • 2 and 3 show a cross section of the planetary reduction gear to which the first embodiment is applied.
  • the planetary bearing device is configured such that the planetary rotating body 11 provided in the planetary speed reducer 10 is supported by a pair of tapered roller bearings 100 disposed between the shafts 13 of the carrier 12.
  • the inner ring spacer 200, the spacer 300, and the outer ring spacer 400 are provided.
  • the planetary speed reducer 10 performs the first speed reduction of the final reduction gear provided inside the wheel rim of the super large dump truck.
  • the super large dump truck is intended for mines and has a load capacity of 300 t or more.
  • the planetary reduction gear 10 is a planetary gear that meshes with both gears 15 and 17 between a sun gear 15 attached to the input shaft 14 and an internal gear 17 fixed to the housing 16.
  • a plurality of planetary rotating bodies 11 are arranged, and each planetary rotating body 11 is rotatably supported by a pair of tapered roller bearings 100 with respect to the shaft 13 of the carrier 12 connected to the output shaft 18.
  • the revolving motion of the planetary rotator 11 revolving while rotating with the gear 17 is output to the output shaft 18 via the carrier 12.
  • An oil bath 19 in which lubricating oil is stored is provided at a lower portion in the housing 16 of the planetary reduction gear 10.
  • the revolving planetary rotor 11 and the tapered roller bearing 100 are immersed in the lubricating oil of the oil bath 19 on the lower side of each, and the lubricating oil flows into the inside of the tapered roller bearing 100 at this time.
  • the diameter of the tapered roller bearing 100 revolving around the sun gear 15 is about 500 mm
  • the revolution speed is about 500 rpm
  • the bearing rotation speed at this time is about 1300 rpm
  • the maximum centrifugal acceleration is about 75 G.
  • the tapered roller bearing 100 includes an outer ring 110, an inner ring 120, a plurality of tapered rollers 130 interposed between the outer ring 110 and the inner ring 120, and a cage 140 that holds these tapered rollers 130.
  • the central axes of the outer ring 110, the inner ring 120, and the retainer 140 are identical in design.
  • the direction along the central axis is simply referred to as “axial direction”
  • the direction perpendicular to the central axis is simply referred to as “radial direction”
  • the circumferential direction around the central axis is simply referred to as “circumferential direction”.
  • the outer ring 110 includes a conical raceway surface 111 formed on the inner periphery, a cylindrical cage guide surface 112 extending in the axial direction from an edge on the small diameter side of the raceway surface 111, and a large diameter side of the raceway surface 111. It has a cylindrical cage guide surface 113 extending in the axial direction from the edge, a small-diameter side surface 114 of the outer ring 110, and a large-diameter side surface 115 of the outer ring 110.
  • the large diameter side of the outer ring 110 refers to the outer ring portion having a larger inner diameter with a radial plane intersecting at the center of the outer ring width, and the small diameter side of the outer ring 110 refers to the radial plane.
  • the cage guide surfaces 112 and 113 and the side surfaces 114 and 115 adjacent to the cage guide surfaces 112 and 113 are chamfered.
  • the inner ring 120 has a conical raceway surface 121 formed on the outer periphery, a large brim 122, and a small brim 123.
  • the large brim 122 guides the large end face of the tapered roller 130.
  • the small brim 123 prevents the tapered roller 130 from falling off the inner ring 120.
  • the tapered roller 130 is interposed between the raceway surfaces 111 and 121 and is in rolling contact therewith.
  • the outer ring 110 is fitted to the inner periphery of the planetary rotating body 11 and rotates integrally with the planetary rotating body 11.
  • the inner ring 120 is fitted to the shaft 13 of the carrier 12 and is stationary with respect to the outer ring 110.
  • the retainer 140 includes a first annular portion 141, a second annular portion 142 having an outer diameter larger than that of the first annular portion 141, and both the annular portions 141, 142 has a column portion 144 that divides the space 142 into pockets 143.
  • the retainer 140 is configured to maintain the circumferential interval between the tapered rollers 130 that fit in the pockets 143 by the pillar portions 144.
  • the cage 140 is guided in the radial direction by the cage guide surfaces 112 and 113 formed on the inner periphery of the outer ring 110.
  • the cage 140 has guided surfaces 145 and 146 that can make sliding contact (guide contact) in the circumferential direction with the cage guide surfaces 112 and 113 of the outer ring 110.
  • the guided surface 145 is formed on the outer periphery of the first annular portion 141.
  • the guided surface 146 is formed on the outer periphery of the second annular portion 142.
  • These guided surfaces 145 and 146 have a cylindrical shape that can face the corresponding cage guide surfaces 112 and 113 in the radial direction with a predetermined guide clearance.
  • the guide clearance and the pocket clearance of the pocket 143 are set so that the maximum eccentric amount of the cage 140 is determined solely by the contact between the inner circumference of the outer ring 110 and the cage 140.
  • the cage 140 may be guided only by contact between the first annular portion 141 and the inner periphery of the outer ring 110, or only by contact between the second annular portion 142 and the inner periphery of the outer ring 110.
  • the guide contact between the pillar portion 144 and the inner periphery of the outer ring 110 may be performed only, or the first annular portion 141, the second annular portion 142 and the guide contact between the pillar portion 144 and the inner periphery of the outer ring 110 may be performed. Also good.
  • the cage 140 can be held when a large centrifugal force acts on the cage 140 due to the rotation / revolution of the planetary rotating body 11.
  • the instrument 140 becomes difficult to tilt.
  • the guiding contact between the cage 140 and the inner circumference of the outer ring 110 is longer in the circumferential direction than when the cage is guided by the inner ring 120 having a shorter circumference than the inner circumference of the outer ring 110. For this reason, the contact pressure at the guide contact portion between the cage guide surfaces 112 and 113 and the guided surfaces 145 and 146 is suppressed as compared with the case where the cage is guided by the inner ring 120. Furthermore, since the sliding speed between the cage guide surfaces 112 and 113 and the guided surfaces 145 and 146 is both guided contact between the outer ring 110 rotating around the shaft 13 and the cage 140, This is smaller than when the cage is guided by the stationary inner ring 120.
  • the second annular portion 142 has a flange 147 protruding to the inner ring 120 side and a groove 148 connected to the entire inner circumference.
  • the flange 147 protrudes in the radial direction over the entire inner circumference of the second annular portion, and improves the rigidity of the second annular portion 142 against the centrifugal force over the entire circumference.
  • the flange 147 is located at the end of the second annular portion 142 and is formed so as to also serve as a groove wall on the bearing outer side of the groove 148. For this reason, the flange 147 and the groove 148 are integrally formed in a hollow shape over the entire circumference.
  • the groove 148 is disposed at a predetermined interval in the axial direction from the pocket 143 in order to ensure the strength in the vicinity of the continuous portion with the column portion 144.
  • the retainer 140 including the first annular portion 141, the second annular portion 142, and the column portion 144 is disposed on the outer ring 110 side of the conical surface including the central axis of the tapered roller 130. For this reason, the lubricating oil easily flows into the inside of the tapered roller bearing 100 from between the inner periphery of the cage 140 and the inner ring 120 or easily escapes to the outside of the bearing.
  • the groove 148 is for increasing the retained amount of lubricating oil in the form of a depression while suppressing the protruding amount of the flange 147 in the radial direction. Even when the groove 148 is omitted and the inner peripheral surface of the column portion 144 is extended to the flange 147, it is possible to form a recess that can receive the lubricating oil.
  • the entire cage 140 is made of resin.
  • the cage made of resin 140 is advantageous in preventing wear of the cage 140 because the friction coefficient of the molding surface is relatively small compared to a cage made of metal such as a steel plate.
  • the rigidity of the roller is relatively soft, and even when the column part 144 is worn, the aggressiveness to the rolling surface of the tapered roller 130 is small, which is advantageous for bearing damage. Aggressiveness to the outer ring 110 and the inner ring 120 due to the centrifugal force resulting from the rotation / revolution motion of the roller 130 is reduced, which is advantageous for bearing damage.
  • the resin examples include polyamide resin (PA), polyacetal (POM), polycarbonate (PC), polyethylene terephthalate (PET), polybutylene terephthalate (PBT), polyetheretherketone (PEEK), and polyphenylene sulfide (PPS). ), Polytetrafluoroethylene (PTFE), polysulfone (PSF), polyethersulfone (PES), polyimide (PI), polyetherimide (PEI), and the like can be used. Moreover, it is good also as glass fiber reinforced resin which mixed glass fiber (GF) with resin, For example, things, such as PA46 + GF and PA66 + GF, are employable.
  • the inner ring spacer 200 is a member that maintains an axial interval between the pair of inner rings 120.
  • the inner ring spacer 200 revolves integrally with the shaft 13 as the planetary rotator 11 revolves.
  • the inner ring spacer 200 has an outer diameter surface 201 whose outer diameter gradually increases toward each of the pair of inner rings 120. Both groove edges of the outer diameter surface 201 formed in the shape of a V-shaped cross section have the same diameter as the outer peripheral edge of the side surface of the adjacent inner ring 120.
  • the lubricating oil pushed in the revolving direction by the outer diameter surface 201 of the revolving inner ring spacer 200 is guided to the outer diameter surface 201 having a V-shaped cross section and smoothly flows to the vicinity of the outer peripheral edge of the side surface of the inner ring 120. For this reason, the lubricating oil easily flows into the bearing of the tapered roller bearing 100.
  • the spacer 300 is a member that contacts the side surface 115 of the outer ring 110 in the axial direction.
  • the spacer 300 rotates integrally with the outer ring 110 and the planetary rotator 11.
  • An inner diameter surface 301 having an inner diameter gradually increasing toward the outer ring 110 is provided.
  • the inner diameter surface 301 has the same diameter as the inner diameter chamfer connected to the side surface 115 of the outer ring 110.
  • the lubricating oil in contact with the inner diameter surface 301 of the rotating spacer 300 is guided to the inner diameter surface 301 and flows smoothly to the vicinity of the inner diameter chamfer of the outer ring 110 by the action of a strong centrifugal force. For this reason, the lubricating oil easily flows into the bearing of the tapered roller bearing 100.
  • the outer ring spacer 400 is a member that maintains an axial interval between a pair of outer rings 110.
  • the outer ring spacer 400 rotates integrally with the outer ring 110 and the planetary rotating body 11.
  • the outer ring spacer 400 includes a base 401 sandwiched between the pair of outer rings 110 and a plurality of protrusions 402 protruding from the base 401 so as to scoop up the lubricating oil.
  • the protrusion 402 has end faces along the axial direction on both sides in the circumferential direction, and the end face can scoop up the lubricating oil.
  • the protruding portion 402 protrudes in the radial direction on the center of the width of the base portion 401.
  • the lubricating oil scooped up by the protruding portion 402 of the rotating outer ring spacer 400 is mainly applied to the inner periphery of the base 401, and smoothly from the inner periphery of the base 401 to the vicinity of the inner diameter chamfer on the side surface 114 side of the outer ring 110. Flowing. For this reason, the lubricating oil easily flows into the bearing of the tapered roller bearing 100.
  • the base 401 has a spiral groove 403 on the inner periphery.
  • the spiral groove 403 has a spiral shape twisted in the circumferential direction toward the axial direction, and reaches the side surface of the outer ring spacer 400.
  • an axial velocity component is given. For this reason, the lubricating oil is more likely to flow toward the outer ring 110.
  • the first embodiment is as described above, and the cage 140 is guided in the radial direction by the inner circumference of the outer ring 110, so that the clearance between the column portion 144 and the tapered roller 130 is as in the rolling element guide system. It is not necessary to set it narrowly, and since the large-diameter second annular portion 142 has the flange 147, the rigidity of the cage 140 is improved. For this reason, 1st Embodiment can prevent the strong contact of the column part 144 and the tapered roller 130, even when the holder
  • the flange 147 protruding toward the inner ring 120 plays a role of pulling up the lubricating oil flowing into the bearing inside the tapered roller bearing 100 and promotes the inflow of lubricating oil into the bearing. Since the cage 140 is arranged close to the outer ring 110 side, the clearance between the inner circumference of the cage 140 and the inner ring 120 is wide, and the lubricating oil flows between the inner circumference of the cage 140 and the inner ring 120. Easy to flow into the bearing through. The inflowing lubricating oil passes through the gap between the column portion 144 of the pocket 143 and the tapered roller 130 toward the outer ring 110 by the action of centrifugal force.
  • the column portion 144 of the retainer 140 and the tapered roller 130 due to centrifugal force. Is improved, and the flowability of the lubricating oil into the inside of the tapered roller bearing 100 is improved, so that the flowing lubricating oil can easily reach the columns 144 and the guided surfaces 145 and 146 of the cage 140. Therefore, abnormal wear of the column portion 144 can be prevented even in a use environment in which strong centrifugal acceleration acts like the first stage of the final reduction gear provided in the drive system of the super large dump truck.
  • the second annular portion 142 has a groove 148 connected to the entire inner periphery, and the flange 147 is formed so as to also serve as the groove wall of the groove 148. While suppressing the protrusion amount, the lubricating oil flowing into the bearing of the tapered roller bearing 100 can be scooped up to increase the amount of lubricating oil retained inside the bearing.
  • the first embodiment includes an inner ring spacer 200 that maintains an axial interval between the pair of inner rings 120, and the inner ring spacer 200 gradually increases in outer diameter toward each of the pair of inner rings 120. Since the outer diameter surface 201 having a V-shaped cross section is provided, the lubricating oil can easily flow smoothly toward the inner rings 120, and can easily flow into the tapered roller bearing 100.
  • the first embodiment includes a spacer 300 that is axially applied to the side surface 115 of the outer ring 110, and the spacer 300 has an inner diameter surface 301 that gradually increases in inner diameter toward the outer ring 110. It is possible to facilitate the smooth flow of oil toward the outer ring 110, and to facilitate the flow of oil into the tapered roller bearing 100.
  • the first embodiment includes an outer ring spacer 400 that maintains an axial distance between the pair of outer rings 110, and the outer ring spacer 400 scoops up lubricating oil with a base 401 sandwiched between the pair of outer rings 110. Since the protrusion 402 protrudes from the base 401, the lubricating oil is scraped up by the protrusion 402, and further smoothly flows from the inner periphery of the base 401 toward the outer ring 110. As a result, the tapered roller bearing 100 It can be made easy to flow into the bearing.
  • the base portion 401 since the base portion 401 has the spiral groove 403 formed on the inner periphery, the lubricating oil applied to the inner periphery of the base portion 401 can be made easier to flow toward the outer ring 110.
  • the lubricating oil can easily flow into the bearing of the tapered roller bearing by various means, the lubricating oil can be enriched inside the bearing, which not only prevents wear but also cools the inside of the bearing with the lubricating oil. It becomes easy. In a usage environment where the lubricating oil that contributes to lubrication tends to become hot and the temperature rise inside the bearing also becomes a problem, it is easy to discharge the lubricating oil inside the bearing to the outside of the bearing, and between the inside and outside of the bearing. It is preferable to suppress the temperature rise by promoting circulation of the lubricating oil.
  • the flange 147 of the second annular portion 142 is provided intermittently in the circumferential direction.
  • An oil groove 149 penetrating in the axial direction is formed between the flanges 147 adjacent in the circumferential direction. Due to the pumping action unique to the tapered roller bearing, the lubricating oil inside the bearing tends to easily flow from the inner ring side to the outer ring side and from the smaller diameter side to the larger diameter side of the outer ring.
  • the cage 150 according to the third embodiment is formed on the outer periphery of the second annular portion 152 and the flange 155 that are shifted in the circumferential direction with respect to the pillar portion 154 that divides the first annular portion 151 and the second annular portion 152 into pockets 153.
  • Oil grooves 156 provided respectively, and oil grooves 157 provided respectively on the outer periphery and the inner periphery of the first annular portion 151 that are shifted in the same manner.
  • the outer peripheral oil groove 156 is recessed so as to divide the guided surface 158 of the second annular portion 152 in the circumferential direction.
  • the oil groove 157 on the outer peripheral side is recessed so as to divide the guided surface 159 of the first annular portion 151 in the circumferential direction.
  • At least one of the first annular portion 151 and the second annular portion 152 is guided around the guided surfaces 158 and 159 that can slide in the circumferential direction on the inner periphery of the outer ring 160 and the guided surfaces 158 and 159. Since it has oil grooves 156 and 157 that are recessed so as to be divided in the direction, it improves the flowability of the lubricating oil up to the guide clearance between the first annular portion and the second annular portion, and prevents oil film breakage at the time of guide contact And the circulation of the lubricating oil between the inside and outside of the bearing can be achieved.
  • the third embodiment employs oil grooves 156 and 157 whose positions in the circumferential direction are shifted with respect to the column portion 154, it is particularly easy to discharge the lubricating oil that has been lubricated and cooled in the pocket 153. Can do.
  • FIG. 7 shows a fourth embodiment as another example.
  • the retainer 170 according to the fourth embodiment has outer peripheries of the first annular portion 171 and the second annular portion 172 except for the column portion 174 that divides the first annular portion 171 and the second annular portion 172 into pockets 173.
  • a spiral oil groove 177 and guided surfaces 175 and 176 are provided. In the figure, both areas of the oil groove 177 are painted black to make the pattern of the oil groove 177 and guided surfaces 175 and 176 easier to see.
  • the oil groove 177 has a spiral shape twisted in the circumferential direction toward the axial direction.
  • an axial speed component is given.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

La présente invention concerne un roulement à rouleaux effilés, lequel roulement, à l'aide d'une cage (140) qui est guidée dans la direction radiale par la périphérie interne d'un chemin de roulement externe (110) et par la disposition d'une bride (147), qui fait saillie vers un chemin de roulement interne (120), sur une seconde section circulaire (142) sur le côté de grand diamètre de la cage (140), empêche un fort contact entre les montants (144) d'une cage (140) et des rouleaux effilés (130) du fait de la force centrifuge, améliore l'écoulement d'entrée d'huile de lubrification à l'intérieur du roulement, et facilite la distribution de ladite huile lubrifiante influente sur les montants (144) et les surfaces guidées (145, 146) de la cage (140), de façon à empêcher une usure anormale des montants (144).
PCT/JP2016/067919 2015-06-18 2016-06-16 Palier à rouleaux effilés et dispositif de palier planétaire WO2016204220A1 (fr)

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JP2015122862A JP2017008987A (ja) 2015-06-18 2015-06-18 円すいころ軸受及び遊星軸受装置
JP2015-122862 2015-06-18

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WO2016204220A1 true WO2016204220A1 (fr) 2016-12-22

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110374991A (zh) * 2019-08-16 2019-10-25 佛山市力普鑫精密技术有限公司 一种旋转精度高的双波线滚珠减速轴承

Citations (5)

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Publication number Priority date Publication date Assignee Title
JP2006125485A (ja) * 2004-10-28 2006-05-18 Ntn Corp 転がり軸受の潤滑装置
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