WO2000075522A1 - Dispositif a palier et procede de fabrication d'un tel dispositif - Google Patents

Dispositif a palier et procede de fabrication d'un tel dispositif Download PDF

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Publication number
WO2000075522A1
WO2000075522A1 PCT/JP2000/003614 JP0003614W WO0075522A1 WO 2000075522 A1 WO2000075522 A1 WO 2000075522A1 JP 0003614 W JP0003614 W JP 0003614W WO 0075522 A1 WO0075522 A1 WO 0075522A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
bearing
bearing device
sleeve
stainless steel
Prior art date
Application number
PCT/JP2000/003614
Other languages
English (en)
Japanese (ja)
Inventor
Susumu Tanaka
Tomohiro Kudo
Katuhiko Tanaka
Manabu Ohori
Original Assignee
Nsk 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 Nsk Ltd. filed Critical Nsk Ltd.
Publication of WO2000075522A1 publication Critical patent/WO2000075522A1/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
    • 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
    • C—CHEMISTRY; METALLURGY
    • C23—COATING METALLIC MATERIAL; COATING MATERIAL WITH METALLIC MATERIAL; CHEMICAL SURFACE TREATMENT; DIFFUSION TREATMENT OF METALLIC MATERIAL; COATING BY VACUUM EVAPORATION, BY SPUTTERING, BY ION IMPLANTATION OR BY CHEMICAL VAPOUR DEPOSITION, IN GENERAL; INHIBITING CORROSION OF METALLIC MATERIAL OR INCRUSTATION IN GENERAL
    • C23C—COATING METALLIC MATERIAL; COATING MATERIAL WITH METALLIC MATERIAL; SURFACE TREATMENT OF METALLIC MATERIAL BY DIFFUSION INTO THE SURFACE, BY CHEMICAL CONVERSION OR SUBSTITUTION; COATING BY VACUUM EVAPORATION, BY SPUTTERING, BY ION IMPLANTATION OR BY CHEMICAL VAPOUR DEPOSITION, IN GENERAL
    • C23C8/00—Solid state diffusion of only non-metal elements into metallic material surfaces; Chemical surface treatment of metallic material by reaction of the surface with a reactive gas, leaving reaction products of surface material in the coating, e.g. conversion coatings, passivation of metals
    • C23C8/06—Solid state diffusion of only non-metal elements into metallic material surfaces; Chemical surface treatment of metallic material by reaction of the surface with a reactive gas, leaving reaction products of surface material in the coating, e.g. conversion coatings, passivation of metals using gases
    • C23C8/08—Solid state diffusion of only non-metal elements into metallic material surfaces; Chemical surface treatment of metallic material by reaction of the surface with a reactive gas, leaving reaction products of surface material in the coating, e.g. conversion coatings, passivation of metals using gases only one element being applied
    • C23C8/20—Carburising
    • C23C8/22—Carburising of ferrous surfaces
    • 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
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/045—Sliding-contact bearings for exclusively rotary movement for axial load only with grooves in the bearing surface to generate hydrodynamic pressure, e.g. spiral groove thrust 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/22—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with arrangements compensating for thermal expansion
    • 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
    • F16C33/12—Structural composition; Use of special materials or surface treatments, e.g. for rust-proofing
    • 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
    • F16C33/14—Special methods of manufacture; Running-in
    • 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
    • F16C2220/00—Shaping
    • F16C2220/60—Shaping by removing material, e.g. machining
    • 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
    • F16C2223/00—Surface treatments; Hardening; Coating
    • F16C2223/10—Hardening, e.g. carburizing, carbo-nitriding
    • F16C2223/12—Hardening, e.g. carburizing, carbo-nitriding with carburizing

Definitions

  • the present invention relates to a bearing device provided with a dynamic pressure bearing (a bearing device provided with a shaft and a sleeve and generating a dynamic pressure between the two to obtain a bearing effect), and particularly for information equipment and audio / visual equipment,
  • the present invention relates to a bearing device used in a spindle motor for a magnetic disk device or an optical disk device.
  • FIG. 7 shows a conventional example of a bearing device provided with a dynamic pressure bearing.
  • the sleeve 4 has a bottom 45 that receives the lower end surface 1 a of the shaft 1.
  • the dynamic pressure grooves 4 1 and 4 2 for radial support are formed on the inner peripheral surface 4 a of the sleeve 4, and the dynamic pressure grooves 30 for axial support are formed on the lower end surface 1 a of the shaft 1. I have.
  • the sleeve 4 is a thin-walled cylinder whose inner diameter increases as the temperature rises. Therefore, if this sleeve is combined with a shaft made of the same material as the sleeve with the same coefficient of thermal expansion, the amount of increase in shaft diameter due to temperature rise will be the same as the amount of increase in sleeve inner diameter, and the operating temperature will change. However, the bearing gap does not change.
  • the sleeve 4 is made of a copper alloy having good machinability
  • the shaft 1 is made of a martensitic stainless steel having a relatively high hardness so that it is hardly damaged during handling. ing.
  • thermal expansion coefficient of copper alloy and martensitic stainless steel coefficient of linear expansion, a copper alloy: 1 7 X 1 0- 6 ⁇ 1 8 X 1 0- 6 (1 / K)
  • martensite G System stainless steel 1 0 x 1 0- 6 ⁇ : L 1 x 1 0- 6 (1 / K)
  • Japanese Patent Application Laid-Open No. H10-893445 discloses an austenitic stainless steel (wire) having a thermal expansion coefficient similar to that of a copper alloy as a shaft material. expansion coefficient: with using a 1 6 X 1 0 one 6 ⁇ 1 7 X 1 0- 6 (1 / ⁇ )), have been proposed to cure the surface of the shaft in nitriding. According to the above-mentioned publication, according to this method, the bearing gap hardly changes in accordance with a change in the operating temperature, and even if the shaft is made of a soft austenitic stainless steel, the surface hardened by nitrogen treatment can be used. However, it is described as having a hardness capable of minimizing scratch wear.
  • the surface of the shaft is hardened by nitriding, so that extremely hard chromium nitride is formed on the surface layer.
  • the corrosion resistance of the shaft surface is reduced compared to the case without nitriding.
  • the hydrodynamic bearing described in the above publication has the following problems due to the low corrosion resistance of the shaft surface.
  • the nitrided shaft surface has low corrosion resistance, and therefore, if this removal step is performed by acid cleaning, the surface may be corroded. In order to avoid corrosion, this removal process must be performed by a mechanical method.However, since the mounting thread is formed at the end of the shaft, the entire surface of the shaft is treated by a mechanical method after nitriding. This requires a great deal of time and money.
  • the present invention has been made in view of such problems of the prior art.
  • a bearing device provided with a dynamic pressure bearing a bearing gap corresponding to a change in operating temperature is provided. It consists of a combination of a copper sleeve and an austenitic stainless steel shaft with little change between the shafts, offering not only high shaft surface hardness but also excellent shaft corrosion resistance.
  • the task is to
  • Another object of the present invention is to improve the start / stop durability of a bearing device including a dynamic pressure bearing by using a shaft having a high surface hardness and a good bearing surface roughness. Disclosure of the invention
  • the present invention provides a bearing device that includes a shaft and a sleeve and generates a dynamic pressure between the two to obtain a bearing action, wherein the shaft is a solution-treated austenitic stainless steel.
  • the bearing surface of the shaft is the surface of the shaft that generates dynamic pressure in cooperation with the sleeve (by interaction with the sleeve), and if the shaft has a dynamic pressure groove, It refers to the portion of the shaft surface where the dynamic pressure groove is formed, and if the sleeve has the dynamic pressure groove, it refers to the portion of the shaft surface that contacts the dynamic pressure groove.
  • austenitic stainless steels examples include SUS303, SUS304, and SUS316. It is preferable to use SUS303 and SUS304 from the viewpoint of machinability, and to use SSUS316 from the viewpoint of corrosion resistance.
  • the bearing surface of the shaft preferably has a surface roughness (R a) of 0.30 / m or less.
  • a preferred embodiment of the bearing device of the present invention is a bearing device that includes a shaft and a sleeve, and generates a dynamic pressure between the two to obtain a bearing effect (a dynamic pressure bearing including a shaft and a sleeve that cooperates with the shaft).
  • the sleeve is made of a copper alloy
  • the shaft is formed by carburizing a shaft made of solution-treated austenitic stainless steel to form a carburized hardened layer on the surface.
  • the bearing surface of the shaft is characterized by having a surface roughness (R a) of not more than 0.30 / m and a surface hardness of not less than H v 400 by removing impurities. Things.
  • the combination of the copper sleeve and the austenitic stainless steel shaft hardly changes the bearing gap in response to changes in operating temperature, while the corrosion resistance of the shaft surface and the start-up of the bearing Hardness (Hv400 or more) and surface roughness sufficient for sliding durability at stop are ensured.
  • the present invention also provides a bearing device comprising a shaft and a sleeve, wherein a dynamic pressure is generated between the two to obtain a bearing effect, wherein the sleeve is made of a martensitic stainless steel or a brittle stainless steel; Is a case in which a carburized hardened layer is formed on the surface of a shaft made of solution-treated austenitic stainless steel by carburizing.
  • a bearing device characterized in that the bearing surface has a surface hardness of Hv 400 or more.
  • Linear expansion coefficient of martensite stainless steel and ferritic stainless steel is a 10 X 10_ 6 ⁇ 1 lxl O- 6 (1 / K), the coefficient of linear expansion of Osute Nai preparative stainless steel (1 6 x 1 0—less than 6 to 17 x 10 (1 / K)). Therefore, a bearing device equipped with a shaft made of austenitic stainless steel and a sleeve made of martensite stainless steel or ferrite stainless steel has a small bearing clearance at high temperatures, so lubrication at high temperatures It is possible to reduce a decrease in bearing rigidity due to a decrease in viscosity of the agent.
  • the carburizing treatment is performed in a carburizing gas atmosphere, for example, by heating to a temperature of 400 to 500 ° C for 10 to 50 hours.
  • Mixed gas as the carburizing gas, CO and H 2 RX gas (CO: 23%, C0 2 1%, H 2: 3 1%, H 2 0: 3 1%, a mixed gas of balance N 2) mixed gas or the like can be used between the C_ ⁇ 2 gas.
  • the carburizing process is performed by using an unsaturated hydrocarbon gas such as It is more preferable to use acetylene or ethylene under a vacuum of not more than ⁇ because a carburized hardened layer where almost no iron-based internal oxide layer is formed is formed. Further, in this method, since Cr 23 C 6 hardly precipitates in the carburized layer, a carburized hardened layer having extremely high corrosion resistance is formed. However, if the carburizing temperature exceeds 500 ° C., precipitation of Cr 23 C 6 occurs, and the corrosion resistance decreases. If the carburizing temperature is lower than 400 ° C, it takes a long time to process. In consideration of these points, the carburizing temperature is preferably set to 400 to 500 ° C.
  • the step of heating and holding in a fluorine-based gas atmosphere is preferably performed under the conditions of a heating temperature of 250 to 450 ° C. and a holding time of 10 minutes to 1 hour.
  • the fluorine gas used include fluorine compound gases such as NF 3 , BF 3 , CF 4 , HF, SF 6 , C 2 F 6 , WF 6 , CHF 3 , SiF 4 , and C 1 F 3.
  • fluorine compound gases such as NF 3 , BF 3 , CF 4 , HF, SF 6 , C 2 F 6 , WF 6 , CHF 3 , SiF 4 , and C 1 F 3.
  • Can be These gases may be used alone, but usually they are diluted with an inert gas such as N 2 gas to about 1 to 10%.
  • NF 3 is the most practical because it is gaseous at room temperature, has high chemical stability, and is easy to handle.
  • the unsaturated hydrocarbon gas it is preferable that a carburized hardened layer is formed on the surface by performing carburizing treatment at a temperature of 400 to 500 ° C. under the above atmosphere and under a vacuum of not more than 200 ° C.
  • FIG. 1 is a schematic sectional view showing a rotary device to which a bearing device according to an embodiment of the present invention is applied.
  • FIG. 2 is a graph showing the results of X-ray diffraction of the surface of No. a-4 test piece before the pickling treatment in the example.
  • FIG. 3 is a graph showing the result of X-ray diffraction of the surface of No. b-2 test piece before pickling treatment in the example.
  • FIG. 4 is a photograph showing a metal structure of a cross-section on the surface side of No. a-4 test piece before pickling treatment in the example.
  • FIG. 5 is a photograph showing a metallographic structure of a cross section on the surface side of a No. b-2 test piece before the pickling treatment in the example.
  • FIG. 6 is a graph showing the result of X-ray diffraction of the surface of No. b-7 test piece before the pickling treatment in the example.
  • FIG. 7 is a schematic sectional view showing an example of a conventional bearing device. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 is a schematic sectional view showing a rotary device to which a bearing device according to an embodiment of the present invention is applied.
  • This rotating device is a spindle motor for a magnetic disk device.
  • the lower part of a shaft 1 is fixed to a base 2, and the upper part of the shaft 1 is arranged in a sleeve 4 fitted inside a hub 3.
  • dynamic pressure grooves 41, 42 for radial support are formed on the inner peripheral surface of the sleeve 4.
  • a receiving surface 43 of a thrust plate 5 fixed to the shaft 1 is formed on an upper portion of the sleeve 4.
  • the dynamic pressure grooves 30 for axial support are formed on the upper and lower surfaces of the thrust plate 5.
  • the bearing surface of the shaft 1 is a portion of the shaft surface that comes into contact with the dynamic pressure grooves 41 and 42.
  • the upper part of this sleeve 4 is closed by a cover plate 6.
  • the cover plate 6 has a through hole 61 into which the shaft 1 is loosely fitted. The end protrudes above this through hole 61.
  • the mouth 7 is fixed to the inner peripheral surface at the lower part of the hub 3, and the stay 8 opposite thereto is fixed to the upper part of the base 2.
  • the sleeve 4 and the thrust plate 5 are made of a copper alloy having good machinability and easy to form a dynamic pressure groove by plastic working (coining).
  • the shaft 1 is formed by forming a solution-processed austenitic stainless steel into a shaft and then carburizing the shaft to form a carburized hardened layer on the surface.
  • the hub 3 is made of aluminum alloy for an aluminum disk, and made of ferritic stainless steel for a glass disk.
  • the spindle motor according to this embodiment includes a bearing device including the shaft 2 and the sleeve 4 corresponding to an embodiment of the present invention. Therefore, in this bearing device, not only is there little change in the bearing clearance according to the change in the operating temperature, but also the corrosion resistance and sufficient hardness of the shaft surface are ensured. As a result, the spindle motor of this embodiment has high reliability and durability.
  • Table 1 below shows the material of each test piece and the heat treatment method.
  • No. a—1 to a—5 and No. b— :! to b—4 are solution-treated austenitic stainless steels (solution treatment conditions: 150 ° C. After heating for 1 hour, water-cooled.) was processed into a rod having a diameter of 5 mm and a length of 5 O mm.
  • Nos. B-5 and b_6 martensite stainless steel processed into the same rod shape as described above was used.
  • a fluorine-based gas After performing the step of heating and holding under an atmosphere, carburizing treatment was performed. That is, first, a test piece was placed in a furnace, and nitrogen and nitrogen fluoride (NF
  • the mixed gas of 3 ) (NF 3 concentration 10%) was introduced and heated and maintained at a temperature of 300 to 380 ° C for 20 to 30 minutes. Then, this test piece was placed in a furnace under a mixed gas atmosphere of RX and C0 2, was subjected to carburizing treatment by holding for 40 hours pressurized heat at a temperature 450 to 500 ° C. As a result, the thickness of the hardened layer formed by carburizing becomes about 20 to 30 / m.
  • a nitriding treatment was performed by heating and holding for 48 hours. As a result, the thickness of the hardened layer formed by the nitriding treatment becomes about 20 to 30 m.
  • test piece was used without heat treatment.
  • Nos. B-5 and b-6 were kept at 950 ° C and 1050 ° C for 30 minutes, oil quenched, and tempered at 160-180 ° C for 2 hours.
  • oxide scale, nitride particles, and soot-like deposits were present on the surface in No. b_l to b-3, and the surface was blackened.
  • the inner oxide layer and soot deposits were present on the surface, and the surface was blackened.
  • Nos. A-4 and a_5 almost no internal oxide layer was observed.
  • the pickling treatment is performed to remove such internal oxide layers and surface deposits.
  • No. bl-b-3 since the base material is significantly eluted by this pickling treatment, the internal oxidation Layers and surface deposits cannot be completely removed.
  • the graph of FIG. 2 shows the result of X-ray diffraction of the surface of No. a-4 test piece before the pickling treatment. From this graph, only the peak of the austenitic stainless steel as the base metal is observed. That is, the carbon is completely dissolved in the monostenite at a concentration lower than the solid solubility limit of the monostenite.
  • Fig. 3 The graph of shows the result of X-ray diffraction of the surface of the No. b_2 test piece before the pickling treatment.
  • the photograph in Fig. 4 shows a cross section of the surface of No. a-4 specimen before pickling.
  • the photograph in Fig. 5 shows a cross section on the surface side of the No. b_2 test piece before the pickling treatment.
  • the surface is very rough, and in addition to clearly seeing the boundary between the compound layer and the base material, cracks and the like are also observed.
  • the surface is gentle and no boundary between the compound layer and the base material is recognized.
  • No. b— After the above heat treatment and pickling treatment, No. b— :! The test pieces of Nos. B-4 to b-6 were not subjected to the pickling treatment after the heat treatment described above, and the test pieces of Nos. B-4 to b-6 were finished by grinding. Each test piece after the processing was subjected to a salt spray test for 2 hours in accordance with JISZ2371. For No. b-7, an annealed SUS303 (without solution treatment) processed into the same rod shape as the other test pieces was prepared. — After the same heat treatment and pickling treatment as in 3, use the same grinding Finishing was performed and a salt spray test was performed under the same conditions.
  • the graph in Fig. 6 shows the result of X-ray diffraction of the surface of No. b-7 specimen before the pickling treatment. From this graph, in addition to the peak of the austenitic stainless steel as the base metal, peaks such as (Cr, Fe) aC and Hiichi Fe are observed. From this result, even if austenitic stainless steel is not used, the reaction between ferrite and carburizing gas occurs during carburizing, and (Cr, Fe) 3 C precipitates unless a solution-treated product is used. I understand.
  • the bearing device equipped with a shaft corresponding to test piece No. a-l to a-5 and a copper alloy sleeve has almost no change in bearing clearance according to the change in operating temperature.
  • the corrosion resistance and sufficient hardness of the shaft surface are ensured, so that the equipment has high reliability and durability.
  • a bearing device equipped with a shaft obtained in the same manner as that of the test pieces No. a-4 and a-5 subjected to vacuum carburization can eliminate the pickling process of the shaft, and therefore the work process There is also an effect that the number can be reduced.
  • the sleeve is made of a copper alloy.
  • the bearing gap is slightly reduced at high temperatures, so In this case, it is possible to reduce a decrease in bearing rigidity due to a decrease in viscosity of the lubricant.
  • the sleeve and the hub are made of stainless steel integrally, and the shaft is made of solution-treated austenitic stainless steel to reduce the bearing stiffness at high temperatures. It can be even smaller.
  • the shaft diameter was 6 mm, and the bearing width (the axial dimension of both hydrodynamic grooves 41 and 42) was 6 mm.
  • the lubricating oil was diester oil and the rotation speed was 7200 rpm.
  • SUS 3 1 6 16. 0 1 0 6 (1 / K).
  • the rotating device shown in Fig. 1 was assembled by combining the shaft and sleeve shown in Table 3.
  • the shaft diameter is 6 mm
  • the bearing width is 6 mm.
  • the shafts of Nos. 21, 22, and 26 were manufactured by using the same SUS303 solution-processed product as a-3 described above and performing the same treatment as a-3.
  • the shaft of No. 23 was prepared by using the same solution-processed SUS 304 as the above-mentioned a-1 and performing the same processing as a-1.
  • the shafts of Nos. 24 and 25 were manufactured using the same solution-processed SUS316 as in a-5 described above, and subjected to the same processing as a-5.
  • the shaft of No. 27 used the same solution-processed SUS303 as b-4 described above, and was used without heat treatment as in b-4.
  • the shaft of No. 28 was manufactured by using the same SUS420J2 as b-5 described above and performing the same processing as b-5.
  • the shaft of No. 29 was manufactured using the same SUS440C as in b-6 described above and by performing the same processing as in b-6.
  • This rotating device was placed sideways, and the rotating device was started and stopped 300,000 times under the conditions of a radial load of 1 N and a rotation speed of 7200 rpm using diester oil as a lubricating oil.
  • Table 3 also shows the observation results.
  • “X” indicates that the degree of damage was extremely large, and “ ⁇ ” indicates that almost no damage occurred.
  • the shaft was made of stainless steel and the sleeve was made of a copper alloy. Are almost the same. In Nos.
  • the shaft is made of austenitic stainless steel and the sleeve is made of ferritic stainless steel, and the thermal expansion coefficient of the sleeve is smaller than that of the shaft.
  • the shaft is made of martensite stainless steel and the sleeve is made of a copper alloy, and the thermal expansion coefficient of the sleeve is larger than that of the shaft.
  • the temperature characteristic value is largest in the combination (No. 22, 25) where the thermal expansion coefficient of the sleeve is smaller than the thermal expansion coefficient of the shaft, and the thermal expansion coefficient of the shaft and the sleeve is almost the same.
  • the same combination (Nos. 21, 23, 24, 26, 27) and the combination (No. 28, 29) with the sleeve's thermal expansion coefficient larger than the shaft's thermal expansion coefficient become smaller.
  • the bearing device of the present invention corrosion resistance and sufficient hardness of the shaft surface are ensured while the shaft is made of austenitic stainless steel having a thermal expansion coefficient substantially equal to that of a copper alloy. .
  • the shaft has a high surface hardness and a good roughness of the bearing surface of the shaft, so that the bearing has excellent durability in starting and stopping and also has excellent corrosion resistance in the shaft. Bearing device is obtained.
  • the bearing gap hardly changes according to the change in the operating temperature.
  • the corrosion resistance and sufficient hardness of the shaft surface are ensured, so that the reliability and durability of the equipment are high.
  • the rigidity of the bearing at high temperatures can be improved by using a combination in which the thermal expansion coefficient of the sleeve is smaller than the thermal expansion coefficient of the shaft.

Abstract

L'invention se rapporte à un dispositif à palier comportant un palier à pression dynamique caractérisé par une variation moins importante du jeu lié à une variation de la température de fonctionnement, ainsi que par une corrosivité et une dureté suffisante à la surface d'un arbre. Ledit dispositif comporte un manchon (4) fabriqué à partir d'un alliage à base de cuivre; l'arbre est fabriqué en acier inoxydable austénitique traité thermiquement par solution et après l'usinage de l'acier inoxydable en un corps d'arbre, le corps de l'arbre est soumis à un traitement de carburation de sorte qu'une couche dure carburée est formée à la surface de l'arbre. Cet arbre doté d'une grande dureté superficielle et présentant une excellente dureté de surface de palier est ensuite utilisé pour accroître la durabilité du dispositif à palier, ledit palier à pression dynamique s'opposant au démarrage et à l'arrêt. Par ailleurs, le coefficient de dilatation thermique du matériau constituant le manchon est rendu inférieur à celui du matériau composant l'arbre de sorte que la rigidité du palier est améliorée à hautes températures.
PCT/JP2000/003614 1999-06-04 2000-06-02 Dispositif a palier et procede de fabrication d'un tel dispositif WO2000075522A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11/158148 1999-06-04
JP15814899 1999-06-04

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004010014A1 (fr) * 2002-07-18 2004-01-29 Yoshinari Yokoo Palier a pression dynamique, moteur a broche, dispositif de lecture de disque et procede de fabrication d'un palier a pression dynamique
JP2004068154A (ja) * 2002-08-01 2004-03-04 Ipsen Internatl Gmbh 部材を黒化するための方法及び装置
JP2006329262A (ja) * 2005-05-24 2006-12-07 Nippon Densan Corp 動圧軸受装置およびこの装置を備えたモータ、並びにこのモータを用いたディスク装置
JP2007046088A (ja) * 2005-08-09 2007-02-22 Yuki Koshuha:Kk 浸窒焼入品及びその製造方法
WO2006109039A3 (fr) * 2005-04-15 2007-05-03 Gsi Group Ltd Arbres de palier a gaz
JP2008544085A (ja) * 2005-06-22 2008-12-04 ダンマークス テクニスケ ウニヴァシティット ディ・ティ・ウ 炭化水素ガス中での浸炭化方法
JP2011190513A (ja) * 2010-03-16 2011-09-29 Tnk Sanwa Precision Co Ltd 摺動部品の製造方法

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JPS62125351U (fr) * 1986-01-31 1987-08-08
JPH09249959A (ja) * 1996-01-09 1997-09-22 Daido Hoxan Inc オーステナイト系金属に対する浸炭処理方法およびそれによって得られたオーステナイト系金属製品
JPH09302456A (ja) * 1996-03-14 1997-11-25 Daido Hoxan Inc 高耐蝕性金属製品およびその製法
JPH1089345A (ja) * 1996-09-10 1998-04-07 Koyo Seiko Co Ltd 動圧軸受
JPH10330906A (ja) * 1997-06-05 1998-12-15 Daido Hoxan Inc オーステナイト系ステンレス製品の製法
JP2000161346A (ja) * 1998-11-27 2000-06-13 Nsk Ltd スピンドルモータ

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JPS62125351U (fr) * 1986-01-31 1987-08-08
JPH09249959A (ja) * 1996-01-09 1997-09-22 Daido Hoxan Inc オーステナイト系金属に対する浸炭処理方法およびそれによって得られたオーステナイト系金属製品
JPH09302456A (ja) * 1996-03-14 1997-11-25 Daido Hoxan Inc 高耐蝕性金属製品およびその製法
JPH1089345A (ja) * 1996-09-10 1998-04-07 Koyo Seiko Co Ltd 動圧軸受
JPH10330906A (ja) * 1997-06-05 1998-12-15 Daido Hoxan Inc オーステナイト系ステンレス製品の製法
JP2000161346A (ja) * 1998-11-27 2000-06-13 Nsk Ltd スピンドルモータ

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004010014A1 (fr) * 2002-07-18 2004-01-29 Yoshinari Yokoo Palier a pression dynamique, moteur a broche, dispositif de lecture de disque et procede de fabrication d'un palier a pression dynamique
US7134791B2 (en) 2002-07-18 2006-11-14 Yoshinari Yokoo Dynamic pressure bearing device, spindle motor, disk drive device, and method of manufacturing dynamic pressure bearing device
JP2004068154A (ja) * 2002-08-01 2004-03-04 Ipsen Internatl Gmbh 部材を黒化するための方法及び装置
WO2006109039A3 (fr) * 2005-04-15 2007-05-03 Gsi Group Ltd Arbres de palier a gaz
GB2440299A (en) * 2005-04-15 2008-01-23 Gsi Group Ltd Gas bearing spindle
GB2440299B (en) * 2005-04-15 2008-10-01 Gsi Group Ltd Gas bearing spindle
JP2006329262A (ja) * 2005-05-24 2006-12-07 Nippon Densan Corp 動圧軸受装置およびこの装置を備えたモータ、並びにこのモータを用いたディスク装置
JP2008544085A (ja) * 2005-06-22 2008-12-04 ダンマークス テクニスケ ウニヴァシティット ディ・ティ・ウ 炭化水素ガス中での浸炭化方法
JP2007046088A (ja) * 2005-08-09 2007-02-22 Yuki Koshuha:Kk 浸窒焼入品及びその製造方法
JP2011190513A (ja) * 2010-03-16 2011-09-29 Tnk Sanwa Precision Co Ltd 摺動部品の製造方法

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