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WO2001063133A1 - Palier fluide de type pression dynamique - Google Patents

Palier fluide de type pression dynamique Download PDF

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Publication number
WO2001063133A1
WO2001063133A1 PCT/JP2001/001182 JP0101182W WO0163133A1 WO 2001063133 A1 WO2001063133 A1 WO 2001063133A1 JP 0101182 W JP0101182 W JP 0101182W WO 0163133 A1 WO0163133 A1 WO 0163133A1
Authority
WO
WIPO (PCT)
Prior art keywords
sleeve
dynamic pressure
fixed shaft
bearing device
seal portion
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2001/001182
Other languages
English (en)
Japanese (ja)
Inventor
Toshifumi Hino
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to US09/959,350 priority Critical patent/US6698931B2/en
Publication of WO2001063133A1 publication Critical patent/WO2001063133A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
    • H02K5/1677—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/086—Structural association with bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly

Definitions

  • the present invention relates to a hydrodynamic bearing device.
  • a spindle motor using a hydrodynamic bearing device has been used for a spare device such as a magnetic disk drive device.
  • a hydrodynamic bearing device that prevents oil leakage has been disclosed.
  • FIG. 5 shows a conventional hydrodynamic bearing device.
  • a thrust plate 4 is attached to one end of a sleeve 3 rotatably supported by a shaft 2 as a fixed shaft, and a thrust bearing 1 attached to the shaft 2 by the sleeve 3 and the thrust plate 4. It is sandwiched with a gap.
  • a seal plate 5 is fixed to the other end of the sleeve 3 by press-fitting, and a minute space is formed between the inner peripheral surface of the seal plate 5 and the shaft 2.
  • the motor hub 6 is bonded to the outer peripheral surface of the sleeve 3 by press fitting.
  • First and second capillaries 7a and 7b are formed at both ends of the space. That is, a V-shaped first capillary seal portion 7a having a taper along the axial direction is formed between the upper end portion of the inner peripheral surface of the sleeve 3 and the shaft 2, and the thrust plate 4 Between the shafts 2, a V-shaped second cavity seal portion b having a tapered surface along the axial direction is formed.
  • the first and second cavity seal portions 7a and 7b are formed as described above, the lubricating oil is held in the bearing by a capillary phenomenon, so that leakage of the lubricating oil can be prevented.
  • At least one of the outer peripheral surface of the shaft 2 and the inner peripheral surface of the sleeve 3 facing the outer peripheral surface, here, the inner peripheral surface of the sleeve 3, is provided with a first capillary seal portion ⁇ a.
  • Herringbone-shaped dynamic pressure generating grooves 8a and 8b are formed in a section between the second cavity seal portion 7b. In FIG. 5, the height is adjusted to the sleeve 3 and the position is shifted sideways.
  • the shape of the dynamic pressure generating groove 8a on the radial bearing surface formed on the inner peripheral surface of the sleeve 3 is such that the width A from the center bent portion 10a to the end 10b of the dynamic pressure generating groove 8a is the center.
  • the shape is formed to be asymmetric so that it is longer than the width B from the bent portion 10a to the end portion 10c.
  • This asymmetric dynamic pressure generating groove is formed in the dynamic pressure generating groove located farthest from the thrust bearing 1.
  • the rotation of the motor causes the force of the lubricating oil to move toward the center of the bearing and the length of the fluid moves, so that the fluid becomes stable. Become.
  • the liquid level of the lubricating oil moves to a position where the balance of the dynamic pressure in the dynamic pressure generating grooves 8a and 8b is balanced, so that part of the dynamic pressure generating grooves 8a and 8b Exposed to the air, the dynamic pressure generating grooves 8a and 8b become easily entrained in the air, and the air enters the bearing.
  • An object of the present invention is to solve the above problems and to provide a hydrodynamic bearing device capable of discharging air mixed in a bearing and preventing lubricating oil from flowing out of the bearing.
  • the hydrodynamic bearing device of the present invention is characterized in that a groove for air release is formed on the outer surface of the fixed shaft.
  • the air mixed in the bearing can be constantly discharged, and the outflow of lubricating oil can be prevented.
  • a thrust plate is attached to one end of a sleeve rotatably supported on a fixed shaft, and the sleeve and the thrust plate are attached to the fixed shaft.
  • the thrust bearing is clamped with a gap in between, and an asymmetrical ring-shaped dynamic bearing is formed on at least one of the outer peripheral surface of the old I1 shaft and the inner peripheral surface of the sleeve facing the outer peripheral surface.
  • a dynamic pressure type floating bearing device in which a pressure generating groove is formed, and a gap between a fixed shaft and an inner peripheral surface of the sleeve and a gap between the sleeve, the thrust plate, and the thrust bearing are filled with lubricating oil.
  • a first taper having a taper extending in the axial direction between one end of the fixed shaft and the sleeve.
  • An air vent groove is formed on an outer surface of the fixed shaft between the one seal portion and the second cavity seal portion.
  • a dynamic pressure floating bearing device is characterized in that, in the first aspect, the groove portion is provided on the side of the second cavity seal portion.
  • a hydrodynamic bearing device is characterized in that, in the second aspect, the groove portion is extended to the second capillary seal portion.
  • the air mixed in the lubricating oil is easily discharged to the outside.
  • the hydrodynamic bearing device according to claim 4 of the present invention is the fluid dynamic bearing device according to any one of claims 1 to 3, wherein the length of the second cavity seal is greater than the length of the first cavity seal. It is characterized by having been lengthened.
  • FIG. 1 shows a hydrodynamic bearing device according to Embodiment 1 of the present invention.
  • Fig. 2 is an illustration of the hydrodynamic grooves formed in the shaft of the hydrodynamic bearing device in Fig. 1.
  • FIG. 3 is a cross-sectional view of a spindle motor using a hydrodynamic bearing device according to Embodiment 2 of the present invention.
  • FIG. 4 is a cross-sectional view of a spindle motor using a hydrodynamic bearing arrangement according to Embodiment 3 of the present invention.
  • FIG. 5 is a metamorphic view of a spindle motor using a conventional hydrodynamic bearing device.
  • FIG. 1 and 2 show a first embodiment of the present invention.
  • the first embodiment differs from the first embodiment in that an air vent groove 9 is provided in the outer peripheral portion of the shaft 2 in order to prevent leakage of lubricating oil, but other configurations are the same as those in FIG. 5 showing a conventional example. .
  • a thrust plate 4 is attached to one end of a sleeve 3 made of brass or the like rotatably supported by a shaft 2 as a fixed shaft, and the sleeve 3 is A thrust bearing 1 attached to the shaft 2 is sandwiched between the thrust plate 4 and the thrust plate 4 with a gap therebetween.
  • a seal plate 5 is inserted into the shaft 2 by press-fitting, and a minute space is formed between the inner periphery of the seal plate 5 and the shaft 2. A small space is formed.
  • the shaft 2 to which the thrust bearing 1 is fixed is inserted into the sleeve 3.
  • a hub 6 is attached to the outer periphery of the sleeve 3 by press fitting.
  • Herringbone-shaped dynamic pressure generating grooves 8 a and 8 b are formed on the inner peripheral surface of the sleeve 3.
  • the dynamic pressure generating groove 8a formed on the upper side has a center bent portion 10a of the dynamic pressure generating groove 8a and a width A up to the end portion 10b of the force generating groove 8a. It has an asymmetric shape longer than the width B from 10a to the end 10c.
  • the lubricating oil generates a force from the upper end of the bearing toward the thrust bearing, so that the moving direction of the oil generated due to the unbalance of the dynamic pressure is regulated, and the level of the lubricating oil is increased. Is stable at a position where the dynamic pressure between 1 O a and 10 b is balanced.
  • the gap between the shaft 2 and the inner peripheral surface of the sleeve 3 and the gap between the sleeve 3 and the thrust plate 4 and the thrust bearing 1 are filled with lubricating oil.
  • a V-shaped first cavity seal portion 7a having a taper extending in the axial direction is formed between the upper end portion of the inner peripheral surface of the sleeve 3 and the shaft 2, and the thrust portion is formed.
  • a V-shaped second cavity seal portion ⁇ b having a taper formed in the axial direction between the plate 4 and the shaft 2 is formed.
  • first capillary seal section 7a and the second capillary seal section 7a A plurality of air vent grooves 9 are formed on the outer surface of the shaft 2 between the shaft portion 7 b and the shaft portion 7 b.
  • the mixed air passes through the air vent grooves 9 and passes through the second air vent groove 9. It is always discharged to the outside from the capillaries seal part 7b.
  • the number of air vent grooves 9 is not particularly limited, and may be one or more.
  • the shape is not particularly limited.
  • FIG. 3 shows a second embodiment of the present invention.
  • the second embodiment is different from the first embodiment in that the air vent groove 9 is extended to the second cavity seal portion 7b, but other configurations are the same as those in the first embodiment.
  • FIG. 4 shows a third embodiment of the present invention.
  • the length of the second capillary seal portion 7b is preferably longer than the length of the first capillary seal portion 7a.
  • the motor is rotated to move the lubricating oil toward the thrust bearing by the asymmetric herringbone-shaped groove 8a formed in the radial bearing, thereby stabilizing the lubricating oil. It is held by the second seal part 7b.
  • the length d2 of the second cavity seal portion 7b is changed to the first cavity seal portion d.
  • the dynamic pressure generating grooves 8a and 8b are formed on the inner peripheral side of the sleeve 3.
  • the present invention is not limited to this. A similar effect can be obtained by forming it on the side of the shaft 2 or by providing both on the shaft 2 and the sleeve 3.
  • the dimension difference between the asymmetrical dynamic pressure generating grooves is 0.2 mm
  • the distance between the sleeve 3 and the shaft 2 is 3 / m
  • eight air vent grooves 9 are formed. It was 0.3 mm in width and 0.3 mm in width.
  • the first cavity seal portion is formed between one end of the fixed shaft and the sleeve, and the other portion of the fixed shaft is connected to the other end of the fixed shaft.
  • Between the end and the thrust plate Forming a second cavity seal portion, and forming an air vent groove on the outer surface of the fixed shaft between the first capillary seal portion and the second capillary seal portion. The air mixed in the bearing is constantly discharged to the outside, preventing the lubricating oil from flowing out.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

L'invention porte sur un palier fluide de type pression dynamique capable d'empêcher les fuites d'huile lubrifiante en évacuant l'air mélangé dans le palier. Selon cette invention, un palier de butée (1) placé sur un arbre fixe (2) est maintenu écarté par un manchon (3) et une plaque de butée (4) est placée sur une extrémité du manchon (3), des gorges asymétriques en arêtes de poisson générant une pression dynamique sont formées dans l'une ou l'autre de la surface périphérique externe de l'arbre fixe (2) ou de la surface périphérique interne du manchon (3), un premier joint d'étanchéité capillaire (7a) est formé entre une extrémité de l'arbre fixe (2) et le manchon (3), un second joint d'étanchéité capillaire est formé entre l'autre extrémité de l'arbre fixe (2) et la plaque de butée (4) et une gorge (9) de purge d'air est formée entre le premier (7a) et le second (7b) joint d'étanchéité capillaire .
PCT/JP2001/001182 2000-02-24 2001-02-19 Palier fluide de type pression dynamique Ceased WO2001063133A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US09/959,350 US6698931B2 (en) 2000-02-24 2001-02-19 Dynamic pressure-type liquid bearing unit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000-46661 2000-02-24
JP2000046661A JP2001234926A (ja) 2000-02-24 2000-02-24 動圧型流体軸受装置

Publications (1)

Publication Number Publication Date
WO2001063133A1 true WO2001063133A1 (fr) 2001-08-30

Family

ID=18569035

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/001182 Ceased WO2001063133A1 (fr) 2000-02-24 2001-02-19 Palier fluide de type pression dynamique

Country Status (5)

Country Link
JP (1) JP2001234926A (fr)
KR (1) KR100480758B1 (fr)
CN (1) CN1120944C (fr)
TW (1) TW470825B (fr)
WO (1) WO2001063133A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003058082A1 (fr) * 2002-01-09 2003-07-17 Minebea Co., Ltd. A Japanese Corporation Procede de fabrication d'un moteur a broche et moteur a broche destine a une unite de disque dur

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4127036B2 (ja) * 2002-12-03 2008-07-30 松下電器産業株式会社 流体軸受装置及びディスク回転装置
JP4625407B2 (ja) 2003-04-24 2011-02-02 パナソニック株式会社 流体軸受装置及びディスク回転装置
CN100422583C (zh) * 2003-04-24 2008-10-01 松下电器产业株式会社 流体轴承装置及磁盘旋转装置
JP4614740B2 (ja) * 2004-11-17 2011-01-19 パナソニック株式会社 スピンドルモータ
CN101225854B (zh) * 2007-01-17 2010-08-25 富准精密工业(深圳)有限公司 动压轴承的制造方法
KR101300338B1 (ko) 2011-07-22 2013-08-28 삼성전기주식회사 스핀들 모터
KR20130058955A (ko) 2011-11-28 2013-06-05 삼성전기주식회사 스핀들 모터 및 그 제조방법
CN103248162B (zh) * 2012-02-01 2015-07-15 日本电产株式会社 主轴马达以及盘驱动装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5806987A (en) * 1996-02-07 1998-09-15 Sankyo Seiki Mfg. Co., Ltd. Hydrodynamic bearing apparatus
JPH11153130A (ja) * 1997-11-21 1999-06-08 Sankyo Seiki Mfg Co Ltd 動圧軸受装置
JPH11159525A (ja) * 1997-11-25 1999-06-15 Nippon Densan Corp 動圧流体軸受装置及び電動機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5806987A (en) * 1996-02-07 1998-09-15 Sankyo Seiki Mfg. Co., Ltd. Hydrodynamic bearing apparatus
JPH11153130A (ja) * 1997-11-21 1999-06-08 Sankyo Seiki Mfg Co Ltd 動圧軸受装置
JPH11159525A (ja) * 1997-11-25 1999-06-15 Nippon Densan Corp 動圧流体軸受装置及び電動機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003058082A1 (fr) * 2002-01-09 2003-07-17 Minebea Co., Ltd. A Japanese Corporation Procede de fabrication d'un moteur a broche et moteur a broche destine a une unite de disque dur

Also Published As

Publication number Publication date
CN1363022A (zh) 2002-08-07
CN1120944C (zh) 2003-09-10
TW470825B (en) 2002-01-01
KR20020006711A (ko) 2002-01-24
JP2001234926A (ja) 2001-08-31
KR100480758B1 (ko) 2005-04-06

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