WO2009107340A1 - Palier de roulement et dispositif à broche l'utilisant - Google Patents

Palier de roulement et dispositif à broche l'utilisant Download PDF

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Publication number
WO2009107340A1
WO2009107340A1 PCT/JP2009/000627 JP2009000627W WO2009107340A1 WO 2009107340 A1 WO2009107340 A1 WO 2009107340A1 JP 2009000627 W JP2009000627 W JP 2009000627W WO 2009107340 A1 WO2009107340 A1 WO 2009107340A1
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WO
WIPO (PCT)
Prior art keywords
rolling bearing
gap
lubricating oil
piece
outer ring
Prior art date
Application number
PCT/JP2009/000627
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English (en)
Japanese (ja)
Inventor
李ソン雨
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 WO2009107340A1 publication Critical patent/WO2009107340A1/fr

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Classifications

    • 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
    • F16C35/08—Rigid support of bearing units; Housings, e.g. caps, covers for spindles
    • F16C35/12—Rigid support of bearing units; Housings, e.g. caps, covers for spindles with ball or roller bearings
    • 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
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • 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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators

Definitions

  • the present invention relates to a rolling bearing with a lubrication mechanism used as grease lubrication for a machine tool spindle and the like, and a spindle apparatus using the same.
  • this air oil lubrication method has a problem from the viewpoint of cost, noise, energy saving, and resource saving because it requires an air oil supply device as ancillary equipment and requires a large amount of air. There is also a problem of deteriorating the environment due to the scattering of oil. In order to avoid these problems, recently, speeding up by grease lubrication has begun to attract attention, and requests are increasing.
  • Patent Document 1 One example of such attempts is Patent Document 1. As shown in FIG. 7, the rolling bearing described in Patent Document 1 is provided with a grease pool forming component 6 having a grease pool 9 formed therein in contact with the stationary race 2 (for example, the outer ring), and this grease pool formation. A gap forming piece 7 extending from the component 6 to the vicinity of the raceway surface 2 a of the fixed side raceway 2 and forming a gap 15 with the fixed side raceway ring 2 is provided, and the grease reservoir 9 and the fixed side raceway ring 2 are The track surface 2 a is communicated with the gap 15.
  • the stationary race 2 for example, the outer ring
  • the base oil of the grease moves to the gap 15 due to the thickener in the grease and the capillary phenomenon of the gap 15.
  • the base oil stored in the clearance 15 is discharged from the clearance 15 due to the temperature change of the stationary-side raceway ring 2 generated by the operation and the air flow generated by the revolution / rotation of the rolling element 3 and fixed. It moves while adhering to the raceway surface 2a of the side raceway ring 2 and is continuously supplied to the rolling element contact portion.
  • the gap amount ⁇ of the gap 15 is very small and the setting allowable range is narrow, it is difficult to adjust.
  • the gap amount ⁇ is very small and the setting allowable range is narrow, it is difficult to adjust.
  • the gap amount ⁇ is too small, the supply of lubricating oil to the raceway surface 2a becomes insufficient.
  • the gap amount ⁇ is too large, the lubricating oil discharged from the gap 15 during operation is added to the grease initially sealed in the bearing, so that the lubricating oil in the bearing space becomes excessive, and the stirring resistance during operation is reduced. growing.
  • the rolling bearing according to the present invention is a rolling bearing having an inner ring, an outer ring, and a plurality of rolling elements interposed between the raceways of the inner and outer rings.
  • An annular gap forming piece that is provided with a step surface that follows the raceway surface in a direction away from the rolling element, and whose tip surface faces the step surface via a gap and forms a flow path between the peripheral wall and the fixed-side raceway.
  • a grease reservoir that communicates with the flow path, and an arcuate piece that closes a portion of the gap between the tip surface and the stepped surface in the circumferential direction is provided on the tip surface of the gap forming piece. It was.
  • the arc-shaped pieces are provided at a plurality of locations in the circumferential direction on the distal end surface of the gap forming piece, and are positioned between adjacent arc-shaped pieces of the gap and are not blocked by the arc-shaped pieces.
  • the rolling bearing device with this configuration is used by filling the grease reservoir and flow passage with grease. Grease is sealed in the bearing space for initial lubrication. As a result, when the bearing is stopped, the base oil in the grease moves from the flow path to the gap due to the thickener in the grease and the capillary phenomenon in the gap, and this capillary phenomenon and the surface tension of the oil combine to cause the base oil in the gap. Is retained oily.
  • the base oil stored in the gap is discharged from the gap due to the temperature change of the fixed side raceway that occurs during operation and the air flow that occurs due to the revolution and rotation of the rolling element, and the base side of the fixed side raceway It moves while adhering to the raceway surface and is continuously supplied to the rolling element contact portion. Therefore, it is possible to achieve high speed, long life and maintenance-free by using the grease sealed in the bearing and the grease sealed in the grease reservoir provided in the bearing.
  • the gap-forming piece is assembled to the stationary side ring so that the tip of the arc-shaped piece contacts the step surface.
  • a gap having a gap amount of is changed.
  • the amount of lubricating oil discharged from the gap can be adjusted. Thereby, it is possible to prevent the lubricating oil in the bearing space from becoming excessive and increase the stirring resistance during operation.
  • Lubricating oil can be supplied in a balanced manner in the circumferential direction by forming the lubricating oil discharge portions at a plurality of locations in the circumferential direction. Moreover, if the circumferential direction range in which the arc-shaped piece is provided is wider than the circumferential range in which the arc-shaped piece is not provided in the tip surface of the gap forming piece, the gap is discharged from the gap. The effect of suppressing the amount of lubricating oil is high, and the amount of lubricating oil can be adjusted appropriately without making the gap extremely narrow. Therefore, processing and assembly of the fixed-side track ring and the gap forming piece are facilitated.
  • the fixed-side race may be an outer ring.
  • the stationary ring is an outer ring
  • the stepped surface is provided on the outer ring, but when the bearing is rotated in a grease-filled state, the sealed grease scatters to the inner diameter of the outer ring by centrifugal force.
  • the connection of the base oil to the wheel is ensured. Therefore, the base oil that is consumed as the lubricating oil in the rolling element contact portion is replenished to the raceway surface from the grease reservoir through the gap, and the lubricating oil is more stably replenished.
  • the lubricating oil discharge part in the gap is preferably located in the lower half of the circumference.
  • a large amount of lubricating oil tends to be unevenly distributed below the gap due to the influence of gravity. If a large amount of lubricating oil is unevenly distributed, the stirring resistance during rotation of the bearing increases. Therefore, the portion where the arc-shaped piece is not provided on the front end surface of the gap forming piece, that is, the lubricating oil discharge portion is positioned in the lower half of the circumference, and the upper half is closed to discharge from the upper half.
  • the lubricating oil discharge part can be formed only at one place on a perpendicular passing through the center of the rolling bearing. Thereby, the effect which prevents that a large amount of lubricating oil discharges biased in the direction of gravity can be expected.
  • the lubricating oil discharge portion is formed at a total of three locations, one on the perpendicular passing through the center of the rolling bearing and two symmetrical with respect to the vertical, and the lubricating oil discharge located at one location on the vertical
  • the cross-sectional area of the portion may be made narrower than the cross-sectional area of the lubricating oil discharge portion located at two locations that are symmetrical with respect to the vertical line.
  • the lubricating oil discharge part located at one position on the perpendicular line, that is, at the lower end of the circumference, is more susceptible to gravity than the lubricating oil discharge parts located at two symmetrical positions across the vertical line.
  • the cross-sectional area of the lower lubricating oil discharge portion is made smaller than the cross-sectional area of the other lubricating oil discharge portions, so that It is preferable that approximately the same amount of lubricating oil be discharged.
  • a main spindle device is a main spindle device that supports a vertical main spindle using the above-described rolling bearing, and has a pair of rolling bearings, and supports the upper and lower portions of the rolling bearing that supports the upper portion of the main shaft.
  • the rolling bearings that provide the gap forming pieces on the lower sides of the bearings and support the upper part of the main shaft are provided with the arc-shaped pieces on the front end surface of the gap forming pieces, rather than the rolling bearings that support the lower part. Wide circumferential range.
  • the rolling bearing that supports the upper portion of the main shaft has a wider circumferential range in which the arc-shaped piece is provided on the tip surface of the gap forming piece than the rolling bearing that supports the lower portion.
  • the wide circumferential range in which the arc-shaped pieces are provided means that the area of the lubricating oil discharge portion in the gap is small.
  • (A) is a side view of the gap forming piece of the rolling bearing that supports the upper part of the spindle of the spindle device
  • (B) is a side view of the gap forming piece of the rolling bearing that supports the lower part. It is sectional drawing of the main axis
  • (A), (B), (C) is a side view of a gap forming piece of a rolling bearing suitable for supporting the main shaft of the main shaft device. It is sectional drawing of the conventional rolling bearing with a lubrication mechanism. It is explanatory drawing which shows the bias
  • Inner ring 1a Raceway surface 2 Outer ring (fixed side raceway) 2a Raceway surface 2b Stepped surface 3 Rolling element 6 Grease pool forming part 7 Gap forming piece 9 Grease pool 10 Outer ring positioning 11 Grease pool forming part main body 14 Channel 15 Clearance 16 Arc-shaped piece 17 Lubricating oil discharge parts 30A, 30B Rolling bearing 31 Spindle
  • this rolling bearing has a plurality of rolling elements 3 interposed between raceways 1a and 2a of an inner ring 1, an outer ring 2, and inner and outer rings 1 and 2, and a grease pool forming component 6 and a gap forming piece. 7.
  • the plurality of rolling elements 3 are held by a cage 4, and one end of the bearing space between the inner and outer rings 1 and 2 is sealed with a seal 5.
  • the seal 5 prevents leakage of grease sealed in the bearing space to the outside.
  • This rolling bearing is an angular ball bearing, the seal 5 is provided at the end on the back side of the bearing, and the grease reservoir forming component 6 and the gap forming piece 7 are provided on the front side of the bearing.
  • the grease reservoir forming component 6 also serves as a seal on the front side of the bearing, so that leakage of grease from the front side of the bearing is prevented.
  • the portion indicated by crossed hatching indicates a portion filled with grease.
  • a step surface 2b following the raceway surface 2a follows the outer ring front side away from the rolling elements 3, that is, the edge on the opposite side to the direction in which the contact angle occurs on the raceway surface 2a. Is provided.
  • the step surface 2 b extends from the raceway surface 2 a to the outer diameter side and faces the outer ring front side, and continues to the inner diameter surface portion 2 c on the front side of the outer ring 2.
  • the grease reservoir forming component 6 is a ring-shaped component having a grease reservoir 9 formed therein, and is provided in contact with the front side width surface of the outer ring 2.
  • the grease reservoir forming component 6 includes an outer ring positioning spacer 10 provided in contact with the front-side width surface of the outer ring 2 and an outward groove-shaped grease reservoir fitted to the inner diameter surface of the outer ring positioning spacer 10. It consists of a molded part body 11. An internal space sandwiched between the outer ring positioning spacer 10 and the grease reservoir forming component main body 11 is a grease reservoir 9.
  • the outer ring positioning spacer 10 has a side wall portion 10a with which the side wall portion 11a of the grease reservoir forming component main body 11 abuts at the end opposite to the outer ring 2 on the inner diameter surface.
  • the grease reservoir forming component main body 11 is axially oriented with respect to the outer ring positioning spacer 10 by bringing the side wall portion 11a into contact with the inside of the side wall portion 10a of the outer ring positioning spacer 10 after the grease is filled in the grease reservoir 9. Is positioned.
  • a sealant (not shown) is interposed between the outer diameter surface of the side wall portion 11a of the grease pool forming component main body 11 and the inner diameter surface of the outer ring positioning spacer 10 opposed thereto, or the grease pool forming component main body 11
  • the outer ring positioning spacer 10 is bonded with an adhesive.
  • a sealing material 21 is interposed between the mating surfaces of the outer ring positioning spacer 10 and the outer ring 2.
  • the sealing material 21 is formed of an O-ring and is fitted in a circumferential groove 22 formed on the mating surface of the outer ring positioning spacer 10. As a result, grease leakage is prevented.
  • the gap forming piece 7 is a ring-shaped member that is disposed along the inner diameter surface portion 2 c of the outer ring 2, has a tip opposed to the step surface 2 b, and forms a flow path 14 and a gap 15 between the outer ring 2. .
  • the gap forming piece 7 is formed integrally with the grease reservoir forming component main body 11. In other words, the grease reservoir forming component main body 11 extends integrally from the outer diameter end portion of the side wall portion 11b on the bearing adjacent side.
  • the flow path 14 is formed by the peripheral wall of the tip 7a of the gap forming piece and the inner diameter surface portion 2c of the outer ring 2 facing this.
  • the gap forming piece 7 has a tip portion 7a extending to a position close to the step surface 2b of the outer ring 2, and the gap forming piece tip portion 7a and the outer ring step surface 2b facing the gap surface are minute in the axial direction.
  • the gap 15 is formed with a small gap amount ⁇ .
  • the gap 15 communicates with the flow path 14 and opens at the end of the track surface 2a.
  • the gap amount ⁇ of the gap 15 is set to 50 to 100 ⁇ m that can cause a capillary action.
  • an arc-shaped piece 16 is provided at the end face of the gap forming piece tip 7a to block a part of the gap 15 between the end face and the stepped surface 2b of the outer ring 2 in the circumferential direction.
  • a location between the arc-shaped pieces 16 becomes the lubricating oil discharge portion 17.
  • the arc-shaped pieces 16 are provided at four locations equally in the circumferential direction.
  • hatched portions are portions where the arc-shaped pieces 16 are present.
  • the optimum value of the phase ⁇ indicating the range on the circumference of each arc-shaped piece 16 varies depending on the location where the rolling bearing is used.
  • the arc-shaped pieces 16 do not necessarily have to be provided at equal intervals, and may be provided in a deviated manner on the circumference. Further, as shown in FIG. 1, in this example, the tip of the arcuate piece 16 is brought into contact with the step surface 2b, but it is not always necessary to make contact.
  • the inner diameter surface following the end face of the gap forming piece tip 7 a is a tapered surface 7 aa close to the rolling element 3, so that the lubricating oil can easily accumulate between the tapered surface 7 aa and the rolling element 3.
  • the distance d between the taper surface 7aa and the rolling element 3 is preferably a minimal gap of 0.2 mm or less with a size that allows oil attached to the taper surface 7aa to transfer to the surface of the rolling element 3.
  • the base 7b of the gap forming piece 7 has a smaller diameter than the tip 7a.
  • a portion surrounded by the outer diameter surface of the base portion 7 b and the inner diameter surface portion 2 c of the outer ring 2 is a part of the grease reservoir 9, and the flow path 14 communicates with the grease reservoir 9.
  • the gap-forming piece 7 is moved to the outer ring 2 so that the tip of the arc-shaped piece 16 contacts the stepped surface 2b of the outer ring 2.
  • the gap 15 having the target gap amount ⁇ can be easily obtained.
  • the cross-sectional area of the lubricating oil discharge portion 17 in the gap 15 can be changed, and the amount of lubricating oil discharged from the gap 15 can be adjusted. For this reason, it is possible to prevent the lubricating oil in the bearing space from becoming excessive and increase the stirring resistance during operation.
  • the inner diameter surface following the end surface of the gap forming piece tip portion 7a is the tapered surface 7aa close to the rolling element 3, the following advantages are obtained. That is, when the distance d between the tapered surface 7aa and the rolling element 3 is large, the grease base oil discharged from the gap 15 is not used as a bearing lubricating oil, but adheres to the outer diameter surface of the grease reservoir forming component body 11. May leak. When the distance d is a minimum gap (0.2 mm or less), oil that flows out while adhering to the outer diameter surface of the grease reservoir forming component body 11 is applied to the surface of the rolling element 3 at the location of the minimum gap. It can be attached and used effectively as a lubricating oil.
  • the fixed-side raceway is the outer ring 2
  • the stepped surface 2b is provided on the outer ring 2
  • the sealed grease is applied to the inner diameter of the outer ring by centrifugal force.
  • the base oil is reliably connected between the gap 15 and the raceway surface 2a.
  • the base oil that is consumed as the lubricating oil in the rolling element contact portion is replenished to the raceway surface 2a from the grease reservoir 9 through the gap 15, and the lubricating oil is more stably replenished.
  • the rolling bearing is an angular ball bearing
  • the stepped surface 2b is formed following the edge on the side opposite to the direction in which the contact angle occurs on the raceway surface 2a.
  • the step surface 2b can be brought close to the center of the rolling element 3, and the lubricating oil can be replenished from the gap 15 to the raceway surface 2a more efficiently.
  • FIG. 3 shows an example of a spindle device for a machine tool using the rolling bearing of the above embodiment.
  • the spindle 31 is of a vertical type, and a lower part and an upper part of the spindle 31 are rotatably supported in a housing 32 by two rolling bearings 30A and 30B.
  • the two rolling bearings 30A and 30B are used in combination with the back surface.
  • the inner ring 1 of each of the rolling bearings 30A and 30B is positioned by an inner ring positioning spacer 36 and an inner ring spacer 37, and is fastened and fixed to the main shaft 31 by an inner ring fixing nut 39.
  • the outer ring 2 is positioned and fixed in the housing 32 by an outer ring positioning spacer 6, an outer ring spacer 40, and outer ring pressing lids 41 and 42.
  • the housing 32 is formed by fitting a housing inner cylinder 32A and a housing outer cylinder 32B, and an oil passage groove 43 for cooling is provided in the fitting portion.
  • the spindle 31 is provided with a chuck (not shown) for detachably attaching a tool or a workpiece (not shown) to the lower end 31a, and the upper end 31b is driven by a rotation transmission mechanism (not shown) such as a motor. ).
  • the motor may be built in the housing 32. This spindle device can be applied to various machine tools such as a machining motor, a lathe, a milling machine, and a grinding machine.
  • both bearings 30A and 30B that is, the upper side of the rolling bearing 30A that supports the upper part of the main shaft 31 and the lower side of the rolling bearing 30B that supports the lower part. Since the gap forming pieces 7 are provided on the respective sides, the amount of lubricating oil discharged from the gap 15 is larger in the upper rolling bearing 30A than in the lower rolling bearing 30B due to the influence of gravity. Therefore, as shown in FIG. 4, the gap forming piece 7 of the rolling bearing 30 ⁇ / b> A that supports the upper part of the main shaft 31 (FIG.
  • FIG. 5 shows a different example of a spindle device for a machine tool using the rolling bearing of the above embodiment.
  • the spindle 31 is a horizontal type, and both ends of the spindle 31 are supported in a housing 32 by two rolling bearings 30A and 30B so as to be rotatable.
  • the structure itself is exactly the same as the vertical type in FIG.
  • FIG. 6A shows an example in which the lubricating oil discharge portion 17 is provided at one place at the lower end on the circumference. Thereby, the effect which prevents that a large amount of lubricating oil discharges biased in the direction of gravity can be expected.
  • FIG. 6B is an example in which lubricating oil discharge portions 17 are provided at two locations on the lower circumference. The two lubricating oil discharge portions 17 are in symmetrical positions across a perpendicular line 19 passing through the center O of the circumference. If there is a possibility of poor lubrication when the lubricating oil discharge part 17 is at one place, the lubricating oil discharge part 17 may be provided at two places in this way.
  • FIG. 6A shows an example in which the lubricating oil discharge portion 17 is provided at one place at the lower end on the circumference. Thereby, the effect which prevents that a large amount of lubricating oil discharges biased in the direction of gravity can be expected.
  • FIG. 6B is an example in which lubricating
  • FIG. 6 (C) shows that the lubricating oil discharge portions 17A, 17B, and 17C are placed at a total of three locations, one at the lower end on the circumference and two at the symmetrical position across the vertical line 19 at the lower portion on the circumference.
  • the lower-lubricating oil discharge portion 17A is more susceptible to gravity than the other lubricating oil discharge portions 17B and 17C, so the cross-sectional area of the lubricating oil discharge portion 17A is larger than the cross-sectional area of the lubricating oil discharge portions 17B and 17C.
  • the rolling bearings 30A and 30B can be increased in speed, extended life and maintenance-free. The effect is exhibited effectively.

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

Abstract

L'invention porte sur un palier de roulement qui a des caractéristiques de vitesse élevée, de longue durée de vie et de non-nécessité d'entretien, obtenues seulement à l'aide de graisse scellée dans le palier, le palier de roulement étant lubrifié de manière efficace. Le palier de roulement comporte une bague interne (1), une bague externe (2) et des corps roulants (3). La bague externe (2) peut être la bague à chemin de roulement immobile. La bague externe (2) a une surface d'épaulement (2b) contiguë à une surface de chemin de roulement (2a) de la bague externe (2) et s'étendant dans la direction à l'opposé des corps roulants (3). Le palier de roulement comporte une pièce de formation d'intervalle (7) ayant une forme annulaire. La pièce de formation d'intervalle (7) comporte une surface d'extrémité avant tournée vers la surface d'épaulement (2b), avec un intervalle (15) entre celles-ci, et a également une paroi périphérique formant un trajet d'écoulement (14) entre la paroi périphérique et la bague externe (2). Le palier de roulement comprend en outre un réservoir de graisse (9) communiquant avec le trajet d'écoulement (14), et comporte également une pièce en arc circulaire (16) au niveau de la surface d'extrémité avant de la pièce de formation d'intervalle (7). La pièce en arc circulaire (16) ferme une partie circonférentielle de l'intervalle (15) entre la surface d'extrémité avant et la surface d'épaulement (2b).
PCT/JP2009/000627 2008-02-29 2009-02-17 Palier de roulement et dispositif à broche l'utilisant WO2009107340A1 (fr)

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JP2008049243A JP2009204139A (ja) 2008-02-29 2008-02-29 転がり軸受、およびそれを用いた主軸装置
JP2008-049243 2008-02-29

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WO2009107340A1 true WO2009107340A1 (fr) 2009-09-03

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Publication number Priority date Publication date Assignee Title
WO2018198213A1 (fr) * 2017-04-26 2018-11-01 日産自動車株式会社 Structure pour ajustement par pression et fixation d'un collier métallique à un élément en résine et procédé de fixation par ajustement par pression

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0522850U (ja) * 1991-08-30 1993-03-26 エヌテイエヌ株式会社 転がり軸受
JP2006132765A (ja) * 2004-10-08 2006-05-25 Ntn Corp 転がり軸受
JP2006308008A (ja) * 2005-04-28 2006-11-09 Jtekt Corp 液体潤滑式円錐ころ軸受装置および車両用ピニオン軸支持装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0522850U (ja) * 1991-08-30 1993-03-26 エヌテイエヌ株式会社 転がり軸受
JP2006132765A (ja) * 2004-10-08 2006-05-25 Ntn Corp 転がり軸受
JP2006308008A (ja) * 2005-04-28 2006-11-09 Jtekt Corp 液体潤滑式円錐ころ軸受装置および車両用ピニオン軸支持装置

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TW200942706A (en) 2009-10-16

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