WO2022163254A1 - 軸受装置及びスピンドル装置 - Google Patents
軸受装置及びスピンドル装置 Download PDFInfo
- Publication number
- WO2022163254A1 WO2022163254A1 PCT/JP2021/048062 JP2021048062W WO2022163254A1 WO 2022163254 A1 WO2022163254 A1 WO 2022163254A1 JP 2021048062 W JP2021048062 W JP 2021048062W WO 2022163254 A1 WO2022163254 A1 WO 2022163254A1
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- WO
- WIPO (PCT)
- Prior art keywords
- lubricant
- rolling bearing
- bearing
- flange portion
- inner ring
- Prior art date
Links
- 239000000314 lubricant Substances 0.000 claims abstract description 150
- 238000005096 rolling process Methods 0.000 claims abstract description 117
- 125000006850 spacer group Chemical group 0.000 claims abstract description 74
- 230000002093 peripheral effect Effects 0.000 claims description 29
- 238000003860 storage Methods 0.000 claims description 29
- 239000004519 grease Substances 0.000 claims description 13
- 238000005520 cutting process Methods 0.000 claims description 3
- 238000005461 lubrication Methods 0.000 abstract description 10
- 239000003921 oil Substances 0.000 description 11
- 230000020169 heat generation Effects 0.000 description 6
- 230000001050 lubricating effect Effects 0.000 description 6
- 230000004048 modification Effects 0.000 description 6
- 238000012986 modification Methods 0.000 description 6
- 238000007599 discharging Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000012423 maintenance Methods 0.000 description 4
- 230000007774 longterm Effects 0.000 description 3
- 238000003756 stirring Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000002452 interceptive effect Effects 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 238000013019 agitation Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
Images
Classifications
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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
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
- B23Q11/12—Arrangements for cooling or lubricating parts of the machine
- B23Q11/121—Arrangements for cooling or lubricating parts of the machine with lubricating effect for reducing friction
- B23Q11/123—Arrangements for cooling or lubricating parts of the machine with lubricating effect for reducing friction for lubricating spindle 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
-
- 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
- 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
- F16C33/6622—Details of supply and/or removal of the grease, e.g. purging grease
-
- 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
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6662—Details of supply of the liquid to the bearing, e.g. passages or nozzles the liquid being carried by air or other gases, e.g. mist 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
- F16N—LUBRICATING
- F16N31/00—Means for collecting, retaining, or draining-off lubricant in or on machines or apparatus
-
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
- F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
-
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
-
- 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
-
- 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
- F16N—LUBRICATING
- F16N2210/00—Applications
- F16N2210/14—Bearings
Definitions
- the present invention relates to improvements in bearing devices and spindle devices.
- oil lubrication such as jet lubrication, oil mist, oil-air lubrication, or grease lubrication has been used for bearing devices that support main spindles of machine tools.
- lean lubrication in which a small amount of lubricating oil adheres to the raceway surface and rolling contact surface of the rolling bearing intermittently at high speed
- lubrication method in which grease is intermittently supplied to the rolling bearing space. It has been developed and has improved performance for high speeds of dmN 1 million or more (dm: rolling bearing pitch circle diameter (mm), N: rotational speed (min ⁇ 1 )).
- a lubricating device that supplies or replenishes a lubricant such as lubricating oil or grease to a bearing as described above, it is important to properly discharge the supplied lubricant to reduce the agitation resistance of the lubricant accompanying the rotation of the spindle. It is an important factor to avoid temperature rise and torque increase of the bearing.
- Patent Document 1 a lubricant supply path for supplying lubricant from the outside to the inside of the angular contact ball bearing, and a discharge spacer as a rotating body arranged near the inner and outer rings on the side surface of the angular contact ball bearing, A bearing device and a spindle device are disclosed in which the lubricant is discharged to the outside of the angular contact ball bearing by the rotation of the discharge spacer.
- the bearing device and the spindle device described in Patent Document 1 are configured to continuously supply the lubricant into the bearing space filled with the lubricant, and further supply the lubricant to push the lubricant out of the bearing. Therefore, the force for discharging the lubricant to the outside of the bearing is small.
- the radial clearance between the discharge flange of the discharge spacer and the end surface of the outer ring of the bearing is specified to be 0.1 to 3 mm (Fig. 1), but the side surface of the discharge flange on the rolling bearing side and the end surface of the outer ring of the bearing are flush with each other.
- Patent Document 1 discloses a configuration in which the discharge collar has a tapered surface, but a sufficient distance cannot be secured between the tip of the tapered surface and the end surface of the bearing outer ring. In other words, it is not possible to secure a sufficient space for storing grease up to the storage space.
- the present invention has been made in view of the above-mentioned problems, and its object is to continuously discharge the supplied lubricant, maintain a good lubricating state, and enable stable continuous operation for a long time. It is an object of the present invention to provide a bearing device and a spindle device that can extend the service life of the bearing and are easy to maintain.
- a bearing device comprising a rolling bearing and an inner ring spacer arranged adjacent to the inner ring of the rolling bearing, wherein lubricant is supplied from the outside to the inside of the rolling bearing via a lubricant supply path.
- the inner ring spacer has a flange formed to protrude radially outward, a root portion of the flange portion is axially separated from an end surface of the inner ring spacer that contacts the inner ring;
- a bearing device according to claim 1 wherein a side surface of the flange portion on the rolling bearing side has a disk-shaped flat surface extending radially outward from a root portion of the flange portion.
- the root portion of the flange portion is axially separated from the end face of the inner ring spacer that contacts the inner ring, and the side surface of the flange portion on the rolling bearing side extends radially from the root portion of the flange portion.
- the supplied lubricant can be continuously discharged, a good lubricating state can be maintained, and long-term continuous operation can be stably performed.
- Either grease or oil is effective as a lubricant, and agitating resistance can be reduced, heat generation can be suppressed, and the service life of the bearing can be extended.
- the spindle device for a machine tool spindle and the spindle device for a high-speed motor of the present invention is rotatably supported by the above-described bearing device. It is possible to suppress the temperature rise and torque increase of the bearing by suppressing it, thereby extending the life of the bearing and facilitating maintenance.
- FIG. 1 is a cross-sectional view of a main part of a bearing device according to a first embodiment of the invention
- FIG. FIG. 7 is a cross-sectional view of a main part of a lubricant discharge structure on the counterbore side of a bearing device according to a first modified example of the first embodiment
- FIG. 6 is a cross-sectional view of a main part of a bearing device according to a second modified example of the first embodiment
- FIG. 11 is a cross-sectional view of a main part of a bearing device according to a third modified example of the first embodiment
- FIG. 5 is a cross-sectional view of a main part of a bearing device according to a second embodiment of the invention
- FIG. 11 is a cross-sectional view of a main part of a bearing device according to a third embodiment of the invention
- FIG. 11 is a cross-sectional view of a main part of a lubricant discharging structure on the counterbore side of a bearing device according to a modified example of the third embodiment
- FIG. 11 is a cross-sectional view of a main part of a bearing device according to a fourth embodiment of the invention
- FIG. 5 is a cross-sectional view of a main part of a bearing device according to a modification of the invention
- 1 is a cross-sectional view showing a spindle device for a machine tool main shaft to which a bearing device of the present invention is applied;
- FIG. 11 is a cross-sectional view showing a spindle device for a machine tool main shaft to which a bearing device of the present invention is applied;
- FIG. 11 is a cross-sectional view showing a spindle device for a machine tool main shaft to which a bearing device
- the bearing device according to each embodiment of the present invention is preferably used in a spindle device for supporting a spindle for a machine tool spindle or a spindle for a high-speed motor such as an AC servomotor.
- FIG. 1 is a cross-sectional view of a main part of a bearing device according to a first embodiment of the invention.
- the bearing device 10 of this embodiment includes a rolling bearing 20, inner ring spacers 30A and 30B arranged on both sides in the axial direction adjacent to the inner ring 21 of the rolling bearing 20, and arranged on both sides in the axial direction adjacent to the outer ring 22.
- a housing 50 in which the outer ring 22 and the outer ring spacers 40A and 40B are fitted; a spindle (rotating shaft) 60 in which the inner ring 21 and the inner ring spacers 30A and 30B are fitted;
- Prepare
- the rolling bearing 20 of this embodiment is an angular contact ball bearing, and includes an inner ring 21, an outer ring 22, and between an inner ring raceway surface (inner ring raceway groove) 21a of the inner ring 21 and an outer ring raceway surface (outer ring raceway groove) 22a of the outer ring 22. a plurality of balls 23 which are rolling elements arranged to be rotatable with a contact angle ⁇ ; and a retainer 24 rotatably holding the plurality of balls 23 .
- the outer ring 22 has a tapered counterbore 25 on its inner peripheral surface on one side in the axial direction with respect to the outer ring raceway surface 22a. 26.
- the axial positions of the axial end surfaces of the inner ring 21 and the outer ring 22 are the same, and no seal member is provided, so that the outer peripheral surface of the inner ring 21 and the inner peripheral surface of the outer ring 22 are separated.
- the bearing space between the surfaces is open to the outside on both sides in the axial direction.
- Each of the inner ring spacers 30A and 30B has a cylindrical portion 35 fitted with the spindle 60 and a flange portion 31 protruding radially outward from the outer peripheral surface of the cylindrical portion 35 .
- a root portion 31a of the flange portion 31 is axially separated from an end face 33 of the cylindrical portion 35 that contacts the inner ring 21, and a side surface 32 of the flange portion 31 on the rolling bearing side extends radially from the root portion 31a of the flange portion 31. It is formed on a disk-shaped flat surface extending along the outward direction.
- the predetermined axial clearance C1 is the axial end surface 22b of the outer ring 22, or It is the same even if it is calculated from any axial end surface of the inner ring 21 (the axial clearance C2 is the same as C1).
- the flange portion 31 of the inner ring spacer 30B closer to the counterbore is formed to have a larger diameter than the flange portion 31 of the inner ring spacer 30A on the counterbore side.
- the outer ring spacers 40A and 40B are provided with a plurality of notches (openings) 41 formed by axially cutting an end face 43 that contacts the outer ring 22 at a plurality of locations in the circumferential direction. Further, on the inner peripheral surfaces of the outer ring spacers 40A and 40B on the rolling bearing side, which overlap with the notch 41 in the axial direction, the rest of the inner A large-diameter portion 42 having a diameter larger than that of the peripheral surface is formed.
- each large-diameter portion 42 is set to the inner diameter of the opposite axial end surfaces of the outer ring 22 so that the lubricant G adhering to the inner peripheral surfaces of both shoulders of the outer ring 22 is easily pushed out of the rolling bearing 20 .
- (hereinafter also referred to as the inner diameter of the end portion) is set to be equal to or greater than Da and Db. Therefore, when the inner diameters of the outer ring spacers 40A and 40B are equal to or greater than the end inner diameters Da and Db of the outer ring 22 and do not interfere with the flange portions 31 of the inner ring spacers 30A and 30B, the large diameter portion 42 It does not have to be formed.
- the housing 50 also includes a pair of lubricant storage spaces 51, 51 formed on the inner peripheral surface, and a lubricant supply path 52 for supplying the lubricant G from the outside to the inside of the rolling bearing 20.
- the lubricant storage space 51 is an annular space formed on the outer peripheral side of the notch 41. Therefore, the bearing space of the rolling bearing 20 consists of the outer peripheral surfaces of the inner ring spacers 30A and 30B and the inner surfaces of the outer ring spacers 40A and 40B. It communicates with the lubricant storage space 51 via the space between the peripheral surface and the notch 41 .
- the lubricant supply path 52 connects the oil supply hole 26 of the outer ring 22 and a lubricant supply portion 201 (see FIG. 10) provided outside.
- the lubricant G supplied from the outside is supplied to the rolling bearing 20 via the lubricant supply path 52 and the oil supply hole 26 of the outer ring 22 .
- the lubricant G is grease
- a predetermined amount of grease is periodically replenished at predetermined intervals.
- the lubricant G supplied to the inside of the rolling bearing 20 lubricates each part of the rolling bearing 20 , and part of it stays inside the rolling bearing 20 .
- the lubricant G that is no longer needed is pushed out of the rolling bearing 20 and discharged, and is discharged to the flanges of the inner ring spacers 30A and 30B arranged in the vicinity of the bearing. It adheres to part 31 .
- the lubricant G adhering to the flange portion 31 is repelled to the outer diameter side by centrifugal force and is forcibly and continuously discharged into the lubricant storage space 51 through the notches 41 of the outer ring spacers 40A and 40B. is stored in the lubricant storage space 51.
- the lubricant G pushed out from the bearing space to the outside in the axial direction is also stored in the space formed in the root portion 31 a of the flange portion 31 , the lubricant G stored in this space also reaches the flange portion 31 . It adheres and is efficiently repelled to the outer diameter side.
- the discharge by the flange portion 31 can balance the supply amount and discharge amount of the lubricant G according to the difference in the rotational speed of the rolling bearing 20 .
- the supply amount of the lubricant G in order to prevent premature damage due to depletion of the lubricant G due to heat generation.
- the lubricant G becomes excessive, which may cause unstable temperature rise and abnormal heat generation.
- the inner ring spacers 30A and 30B (flange portion 31) rotate at high speed, the centrifugal force is large, and the discharge amount of the lubricant G is increased accordingly.
- An appropriate amount of lubricant G can be retained inside and near the rolling bearing 20 without increasing the amount of the lubricant G remaining inside.
- Either grease or oil is effective as the lubricant G, and heat generation can be suppressed by reducing stirring resistance. Further, when the lubricant storage space 51 is filled with the lubricant G, it is necessary to discharge the lubricant to the outside of the bearing device 10. By providing a discharge passage (not shown) that communicates the space and sucking it from the outside, most of the lubricant G can be discharged, which facilitates maintenance. In particular, in the case of oil replenishment lubrication, the discharge passage with the external space is effective.
- the flange portion 31 of the inner ring spacers 30A, 30B effectively discharges the lubricant G by the so-called slinger effect.
- the slinger effect means that the peripheral speed on the outer diameter side of the flange portion 31 becomes faster than the peripheral speed on the inner diameter side. Refers to the effect of air flow toward the radial side.
- the side surface 32 of the flange portion 31 on the rolling bearing side may be provided with a slit, a spiral groove, or other unevenness that accelerates the fluidity of the lubricant.
- a slit, a spiral groove, or other unevenness that accelerates the fluidity of the lubricant.
- the lubricant G supplied to the inside of the rolling bearing 20 is applied to the side surface 32 of the flange portion 31 on the side of the rolling bearing and the axial end surface 22b of the outer ring 22. It is pushed out of the rolling bearing 20 by the axial clearances C1 and C2 between the rolling bearings 20 and is discharged.
- the lubricant is flipped to the side and stored in the lubricant storage space 51 . Further, the lubricant is discharged from the storage space 51 to the outside through a discharge passage.
- FIG. 2 is a cross-sectional view of the main part of the lubricant discharge structure on the counterbore side of the bearing device according to the first modification of the first embodiment.
- the lubricant G discharged from the rolling bearing 20 is sufficiently stored in the space formed between the outer peripheral surface of the inner ring spacer 30A and the inner peripheral surface of the outer ring spacer 40A due to the axial clearance C1.
- the lubricant G adhering to the flange portion 31 can be flipped off to the outer diameter side by the action of the centrifugal force and discharged into the lubricant storage space 51 .
- the large-diameter portion 42 of the outer ring spacer 40A extends beyond the axial end surface 41a of the notch 41. It is formed up to the direction position.
- the outermost diameter portion of the side surface 32 on the rolling bearing side of the flange portion 31 and the extension line L1 of the side surface 32 are arranged closer to the rolling bearing 20 than the axial end surface 41a of the notch 41 (that is, ⁇ 1>0 ).
- the lubricant G adhering to the flange portion 31 and flipped off is reliably discharged to the lubricant storage space 51 via the notch 41 .
- An axial end face 51a of the lubricant storage space 51 having a rectangular cross section away from the rolling bearing 20 is formed at the same axial position as the axial end face 41a of the notch 41. The lubricant is reliably discharged into the lubricant storage space 51 .
- the layout of the flange portion 31 of this modified example may be applied to the side opposite to the counterbore.
- FIG. 3 is a cross-sectional view of a main part of a bearing device according to a second modified example of the first embodiment.
- the flange portion 31 and the notch 41 are formed only in the inner ring spacer 30A and the outer ring spacer 40A on the side where the counterbore is formed in the axial direction, and the lubricant storage space 51 of the housing 50 is also formed. It is formed on the counterbore side.
- the bearing space between the outer peripheral surface of the inner ring 21 and the inner peripheral surface of the outer ring 22 is wider on the counterbore side than on the counterbore side, and the amount of the lubricant G stored on the counterbore side is large, resulting in rolling.
- the amount of lubricant G discharged to the outside of the bearing also increases. Therefore, the flange portion 31 and the notch 41 may be provided only on the counterbore side.
- FIG. 4 is a cross-sectional view of a main part of a bearing device according to a third modified example of the first embodiment.
- the rolling bearing 20 may have a straight-shaped counterbore 25A with the same inner diameter of the inner peripheral surface along the axial direction, like this bearing device 10c.
- the lubricant G supplied to the inside of the rolling bearing is discharged to the outside of the rolling bearing, and the lubricant G adhering to the flange portion 31 of the inner ring spacers 30A and 30B is removed by centrifugal force. It is flipped to the side and is forcibly and continuously stored in the lubricant storage space 51 .
- the outer diameter Dfa of the flange portion 31 of the inner ring spacer 30A is set larger than the end inner diameter Da of the counterbore 25A.
- the outer diameter Dfb of the flange portion 31 of the inner ring spacer 30B is also set larger than the end inner diameter Db on the counterbore side.
- the outer diameters Dfa and Dfb of the flange portion 31 are large, the peripheral speed of the outer peripheral portion of the flange portion 31 increases, and the magnitude of the centrifugal force that repels the lubricant G increases, thereby ensuring the lubricant G. can be discharged to Other configurations and actions are the same as those of the first embodiment.
- a bearing device according to a third embodiment will be described with reference to FIG.
- a tapered portion 34 axially spaced apart from the rolling bearing 20 radially outward is formed on the outer diameter side portion of the rolling bearing side side surface 32 of the flange portion 31 of the inner ring spacers 30A and 30B.
- the axial gaps C1 and C2 between the side surface of the flange portion 31 on the side of the rolling bearing and the axial end surface of the rolling bearing 20 are increased on the outer diameter side of the flange portion 31, and the lubricant G is pushed out from the rolling bearing 20. can be easily discharged.
- the lubricant G adhering to the side surface 32 of the flange portion 31 on the rolling bearing side is displaced radially outward along the disk-shaped flat surface and the tapered portion 34 of the side surface 32 on the rolling bearing side of the flange portion 31 due to centrifugal force.
- the tapered portion 34 does not necessarily have to be a conical surface, and may have a gently curved surface. Other configurations and actions are the same as those of the first embodiment.
- FIG. 7 is a cross-sectional view of a main part of a lubricant discharge structure on the counterbore side of a bearing device according to a modification of the third embodiment.
- the flange portion 31 has C1 in the range of 0.5 to 50 mm. 22 is formed so as to ensure a larger axial clearance C1 between the axial end faces 22b.
- the lubricant G discharged from the rolling bearing 20 is sufficiently stored in the space formed between the outer peripheral surface of the inner ring spacer 30A and the inner peripheral surface of the outer ring spacer 40A due to the axial clearance C1.
- the lubricant G adhering to the flange portion 31 can be flipped off to the outer diameter side by the action of the centrifugal force and discharged into the lubricant storage space 51 .
- the large diameter portion 42 of the outer ring spacer 40A also extends beyond the axial end face 41a of the notch 41. It is formed up to the direction position.
- the flange portion 31 also has a tapered portion 34 on the outer diameter side portion of the side surface 32 on the rolling bearing side, but the axial position of the outermost diameter portion of the tapered portion 34 is the axial end surface of the notch 41 .
- the contact angle ⁇ is set so that it is closer to the rolling bearing 20 than 41a (that is, ⁇ 2>0).
- the lubricant G adhering to the flange portion 31 and flipped off is reliably discharged to the lubricant storage space 51 via the notch 41 .
- the layout of the flange portion 31 of this modified example may also be applied to the counterbore side.
- the retainer 24 of the rolling bearing 20 has an inclined surface 24a on its outer peripheral surface whose diameter gradually increases with distance from the center of the rolling bearing 20 in the axial direction.
- the lubricant G supplied through the lubricant supply path 52 and the oil supply hole 26 of the outer ring 22 and stored in the rolling bearing 20 is moved to the inclined surface 24a by the centrifugal force caused by the rotation of the retainer 24. It is guided radially and axially outward along the rim, is discharged from the rolling bearing 20 to the outside, and easily adheres to the flange portion 31 .
- the lubricant G adhering to the flange portion 31 is repelled radially outward by centrifugal force and stored in the lubricant storage space 51 , so the lubricant G can be discharged from the rolling bearing 20 more efficiently.
- Other configurations and actions are the same as those of the first embodiment.
- angular contact ball bearings are used, but the rolling bearing of the present invention is not limited to this.
- a cylindrical roller bearing may be used as the rolling bearing 120, as in a bearing device 10h shown in FIG. be able to. That is, in the rolling bearing 120 as well, the inner ring 121 is arranged between the inner ring spacers 30A and 30B having the flange portion 31, the outer ring 122 is arranged between the outer ring spacers 40A and 40B having the notch 41, and The outer ring 122 has an oil supply hole 126 penetrating in the radial direction to supply the lubricant G from the lubricant supply path 52 into the bearing space.
- the shape of the rolling bearing 120 is symmetrical, the shape of the flange portion 31 of the inner ring spacers 30A, 30B may also be the same.
- FIG. 10 is a cross-sectional view showing a machine tool spindle device 200 to which the bearing device 10 of the embodiment described above is applied.
- the spindle device 200 is of a motor built-in type. is rotatably supported with respect to the housing 50 by .
- the housing 50 is formed with a plurality of lubricant supply paths 52 communicating from the rear of the housing 50 in the axial direction to the oil supply holes 26, 126 of the outer rings 22, 122 of the bearings 20, 120, respectively.
- a lubricant supply portion 201 is provided outside the housing 50, and an opening 202 for passing a pipe from the lubricant supply portion 201 or a lubricant supply portion is provided in the axial rear end surface of the housing 50.
- a relay joint or the like for relaying the piping from 201 is provided. Therefore, the lubricant is supplied to the plurality of angular ball bearings 20 via the plurality of lubricant supply paths 52 by connecting the lubricant supply portion 201 to the opening 202 .
- Lubricant supply to cylindrical roller bearing 120 is performed by connecting lubricant supply portion 201 to opening 203 provided in the axial rear end surface of outer ring spacer 40A and communicating hole 204 formed in outer ring spacer 40A. through a lubricant supply 52 including
- the housing 50 is formed with a pair of lubricant storage spaces 51, 51 on inner peripheral surfaces on both axial sides corresponding to the bearings 20, 120, respectively.
- Inner ring spacers 30A, 30B and outer ring spacers 40A, 40B located on both sides in the axial direction of bearings 20, 120 are formed with flanges 31, 31 and notches 41, 41, respectively.
- a bearing device comprising a rolling bearing and an inner ring spacer arranged adjacent to the inner ring of the rolling bearing, wherein lubricant is supplied from the outside to the inside of the rolling bearing via a lubricant supply path.
- the inner ring spacer has a flange formed to protrude radially outward, a root portion of the flange portion is axially separated from an end surface of the inner ring spacer that contacts the inner ring;
- the root portion of the flange portion is axially separated from the end surface of the inner ring spacer that contacts the inner ring, and the side surface of the flange portion on the rolling bearing side extends radially from the root portion of the flange portion.
- the opening is formed by axially cutting out a portion of the outer ring spacer in the circumferential direction from the end face that contacts the outer ring,
- the bearing device according to (2) wherein the outermost diameter portion of the side surface of the flange portion facing the rolling bearing is located closer to the rolling bearing than the axial end surface of the opening. According to this configuration, the lubricant adhering to the flange can reliably pass through the opening.
- an axial clearance between a side surface of the flange portion on the rolling bearing side and an axial end surface of the rolling bearing is 0.5 mm to 50 mm. bearing device. According to this configuration, the lubricant in the rolling bearing can be discharged to the outside, and the lubricant can be adhered to the flange.
- a spindle device for a machine tool spindle wherein the spindle is rotatably supported by the bearing device according to any one of (1) to (8). According to this configuration, the spindle of the spindle device for machine tool main shaft rotating at high speed can be supported by the bearing having a long service life, which facilitates maintenance.
- a spindle device for a high-speed motor wherein the spindle is rotatably supported by the bearing device according to any one of (1) to (8).
- the spindle of the spindle device for a high-speed motor that rotates at high speed can be supported by the bearing having a long service life, which facilitates maintenance.
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Abstract
Description
排出間座の回転によって潤滑剤をアンギュラ玉軸受の外部へ排出するようにした軸受装置およびスピンドル装置が記載されている。これにより、長時間の連続運転が安定して可能となり、良好なグリース潤滑状態を保つことで軸受の長寿命化が図られている。
また、特許文献1には、排出つばがテーパ面を有する構成が開示されているが、テーパ面の先端と軸受外輪端面との間に、十分な距離を確保することができない。つまり、貯蔵空間に至るまでのグリースを収容する空間を十分に確保することができない。
(1) 転がり軸受と、前記転がり軸受の内輪に隣接して配置された内輪間座と、を備え、潤滑剤供給経路を介して外部から前記転がり軸受の内部へ潤滑剤を供給する軸受装置であって、
前記内輪間座は、径方向外方に突出して形成されるつば部を備え、
前記つば部の根元部は、前記内輪と当接する前記内輪間座の端面から軸方向に離間し、
前記つば部の前記転がり軸受側の側面は、前記つば部の根元部から径方向外方に沿って延びる円盤状の平坦面を有する、ことを特徴とする軸受装置。
図1は、本発明の第1実施形態に係る軸受装置の要部断面図である。本実施形態の軸受装置10は、転がり軸受20と、転がり軸受20の内輪21に隣接して軸方向両側に配置された内輪間座30A,30Bと、外輪22に隣接して軸方向両側に配置された外輪間座40A,40Bと、外輪22及び外輪間座40A,40Bが内嵌されるハウジング50と、内輪21及び内輪間座30A,30Bが外嵌されるスピンドル(回転軸)60と、を備える。
また、本実施形態の転がり軸受20は、内輪21及び外輪22の各軸方向端面の軸方向位置が同じであり、また、シール部材を有さず、内輪21の外周面と外輪22の内周面との間の軸受空間を軸方向両側で外部に開放した構成としている。
これにより、内輪間座30A,30Bのつば部31と転がり軸受20の軸方向端面(外輪22の軸方向端面22b)との間には、つば部31の転がり軸受側の側面32と転がり軸受20の軸方向端面との間に所定の軸方向隙間C1、C2を持った空間が、内輪間座30A,30Bの円筒部35aの外周面から外径側に亘って形成される。
なお、転がり軸受20は、外輪幅と内輪幅が公差範囲内でほぼ同一なものを採用しているため、本実施形態において、所定の軸方向隙間C1は、外輪22の軸方向端面22b、又は内輪21の軸方向端面のいずれから起算しても同じである(軸方向隙間C2もC1と同様)。
また、本実施形態では、カウンタボア寄りの内輪間座30Bのつば部31は、反カウンタボア側の内輪間座30Aのつば部31よりも大径に形成されている。
なお、各大径部42の内径は、外輪22の両肩部の内周面に付着した潤滑剤Gが転がり軸受20の外部に押し出されやすいように、外輪22の対向する軸方向端面の内径(以下、端部内径とも称する)Da,Db以上に設定されている。
しがたって、外輪間座40A,40Bの内径が、外輪22の端部内径Da,Db以上で、且つ、内輪間座30A,30Bのつば部31と干渉しない場合には、大径部42が形成されなくてもよい。
なお、断面矩形状の潤滑剤貯蔵空間51の転がり軸受20から離れた軸方向端面51aは、切り欠き41の軸方向端面41aと同一な軸方向位置に形成されており、切り欠き41を介して潤滑剤貯蔵空間51へ確実に排出される。
また、この変形例のつば部31のレイアウトは、反カウンタボア側にも適用されてもよい。
この場合も、転がり軸受の内部に供給された潤滑剤Gは、転がり軸受の外部へ排出されるとともに、内輪間座30A,30Bのつば部31に付着した潤滑剤Gは、遠心力で外径側へ弾き飛ばされて、強制的かつ継続的に潤滑剤貯蔵空間51に貯蔵される。
次に、図5を参照して、第2実施形態の軸受装置について説明する。この軸受装置10dでは、内輪間座30Aのつば部31の外径Dfaが、カウンタボア25Aの端部内径Daより大きく設定されている。同様に、内輪間座30Bのつば部31の外径Dfbも、反カウンタボア側の端部内径Dbより大きく設定されている。
その他の構成及び作用については、第1実施形態のものと同様である。
次に、図6を参照して、第3実施形態の軸受装置について説明する。この軸受装置10eでは、内輪間座30A、30Bのつば部31の転がり軸受側の側面32の外径側部分に、径方向外方に向かって転がり軸受20から軸方向に離間するテーパ部34を備える。これにより、つば部31の転がり軸受側の側面と転がり軸受20の軸方向端面との軸方向隙間C1,C2がつば部31の外径側で大きくなり、転がり軸受20から押し出された潤滑剤Gを容易に排出できる。また、つば部31の転がり軸受側の側面32に付着した潤滑剤Gは、遠心力により、つば部31の転がり軸受側の側面32の円盤状の平坦面及びテーパ部34に沿って径方向外方に案内されて、確実に潤滑剤貯蔵空間51へ排出され、排出性が向上する。なお、テーパ部34は、必ずしも円すい面とする必要はなく、緩やかな曲面状とすることも可能である。
その他の構成及び作用については、第1実施形態のものと同様である。
なお、この変形例のつば部31のレイアウトも、反カウンタボア側にも適用されてもよい。
次に、図8を参照して、第4実施形態の軸受装置について説明する。この軸受装置10gでは、転がり軸受20の保持器24は、外周面に、転がり軸受20の中心から軸方向に離間するに従って、次第に大径となる傾斜面24aを有する。これにより、潤滑剤供給経路52及び外輪22の給油孔26を介して供給されて転がり軸受20内に貯留する潤滑剤Gは、保持器24の回転に伴う遠心力の作用により、傾斜面24aに沿って径方向及び軸方向外方に案内され、転がり軸受20から外部に排出され、つば部31に付着しやすくなる。つば部31に付着した潤滑剤Gは、遠心力によって径方向外方に弾き飛ばされて潤滑剤貯蔵空間51に貯蔵されるので、より効率的に潤滑剤Gを転がり軸受20から排出できる。
その他の構成及び作用については、第1実施形態のものと同様である。
したがって、複数のアンギュラ玉軸受20への潤滑剤供給は、開口部202に潤滑剤供給部201が接続されることで、複数の潤滑剤供給経路52を介して行われる。また、円筒ころ軸受120への潤滑剤供給は、潤滑剤供給部201が外輪間座40Aの軸方向後端面に設けられた開口部203に接続され、外輪間座40Aに形成された連通孔204を含む潤滑剤供給部52を介して行われる。
(1) 転がり軸受と、前記転がり軸受の内輪に隣接して配置された内輪間座と、を備え、潤滑剤供給経路を介して外部から前記転がり軸受の内部へ潤滑剤を供給する軸受装置であって、
前記内輪間座は、径方向外方に突出して形成されるつば部を備え、
前記つば部の根元部は、前記内輪と当接する前記内輪間座の端面から軸方向に離間し、
前記つば部の前記転がり軸受側の側面は、前記つば部の根元部から径方向外方に沿って延びる円盤状の平坦面を有する、ことを特徴とする軸受装置。
この構成によれば、つば部の根元部は、内輪と当接する内輪間座の端面から軸方向に離間し、つば部の転がり軸受側の側面は、つば部の根元部から径方向に沿って延びる円盤状の平坦面を有することで、潤滑剤の供給により、転がり軸受の内部に滞留する潤滑剤は、転がり軸受の外部へ押し出されて排出されるとともに、内輪間座のつば部に付着した潤滑剤は、遠心力で外径側へ弾き飛ばされて、強制的かつ継続的に軸受外部へ排出される。これにより、供給された潤滑剤を継続的に排出でき、良好な潤滑状態を保って、長時間の連続運転が安定して可能となる。
前記転がり軸受の外輪に隣接して配置され、前記貯蔵空間に連通する開口部を備える外輪間座と、
をさらに備え、
前記開口部は、前記内輪間座のつば部の径方向外側に形成される、(1)に記載の軸受装置。
この構成によれば、転がり軸受から排出された潤滑剤を、外輪間座の開口部を介してハウジングの貯蔵空間に貯蔵できる。
(3) 前記開口部は、前記外輪間座の円周方向の一部を、前記外輪と当接する端面から軸方向に切り欠くことで形成され、
前記つば部の前記転がり軸受側の側面の最外径部は、前記開口部の軸方向端面よりも前記転がり軸受側に位置する、(2)に記載の軸受装置。
この構成によれば、つば部に付着した潤滑剤が、開口部内を確実に通過させることができる。
この構成によれば、転がり軸受内の潤滑剤を、外部に排出でき、また、潤滑剤をつば部に付着させることができる。
この構成によれば、つば部に付着した潤滑剤を、効率よく排出できる。
この構成によれば、外輪の内周面に沿って転がり軸受の外部に排出される潤滑剤もつば部の転がり軸受側の側面に付着しやすくなり、付着した潤滑剤は外径側に弾き飛ばされるので、潤滑剤の排出性をより向上させることができる。
この構成によれば、保持器に付着した潤滑剤を、遠心力により転がり軸受から外部へ効率よく排出できる。
この構成によれば、グリース潤滑される転がり軸受を良好な潤滑状態に維持できる。
この構成によれば、高速回転する工作機械主軸用スピンドル装置のスピンドルを、長寿命化が図られた軸受により支持でき、メンテナンスが容易となる。
この構成によれば、高速回転する高速モータ用スピンドル装置のスピンドルを、長寿命化が図られた軸受により支持でき、メンテナンスが容易となる。
20,120 転がり軸受
21 内輪
22 外輪
24 保持器
24a 傾斜面
30A,30B 内輪間座
31 つば部
32 転がり軸受側の側面
33 内輪と当接する端面
34 テーパ部
35 円筒部
40A,40B 外輪間座
41 切り欠き(開口部)
50 ハウジング
51 潤滑剤貯蔵空間
52 潤滑剤供給経路
60 スピンドル
C1,C2 つば部の転がり軸受側の側面と転がり軸受の軸方向端面との軸方向隙間
Da,Db 外輪の端部内径
Dfa,Dfb つば部の外径
G 潤滑剤
Claims (10)
- 転がり軸受と、前記転がり軸受の内輪に隣接して配置された内輪間座と、を備え、潤滑剤供給経路を介して外部から前記転がり軸受の内部へ潤滑剤を供給する軸受装置であって、
前記内輪間座は、径方向外方に突出して形成されるつば部を備え、
前記つば部の根元部は、前記内輪と当接する前記内輪間座の端面から軸方向に離間し、
前記つば部の前記転がり軸受側の側面は、前記つば部の根元部から径方向外方に沿って延びる円盤状の平坦面を有する、ことを特徴とする軸受装置。 - 前記転がり軸受の外輪が内嵌されると共に、排出された前記潤滑剤を貯蔵可能な貯蔵空間を有するハウジングと、
前記転がり軸受の外輪に隣接して配置され、前記貯蔵空間に連通する開口部を備える外輪間座と、
をさらに備え、
前記開口部は、前記内輪間座のつば部の径方向外側に形成される、請求項1に記載の軸受装置。 - 前記開口部は、前記外輪間座の円周方向の一部を、前記外輪と当接する端面から軸方向に切り欠くことで形成され、
前記つば部の前記転がり軸受側の側面の最外径部は、前記開口部の軸方向端面よりも前記転がり軸受側に位置する、請求項2に記載の軸受装置。 - 前記つば部の前記転がり軸受側の側面と、前記転がり軸受の軸方向端面との軸方向隙間は、0.5mm~50mmである、請求項1~3のいずれか1項に記載の軸受装置。
- 前記つば部の前記転がり軸受側の側面は、径方向外方に向かって前記転がり軸受から軸方向に離間するテーパ部を備える、請求項1~4のいずれか1項に記載の軸受装置。
- 前記つば部の外径は、前記転がり軸受の外輪の内径より大きい、請求項1~5のいずれか1項に記載の軸受装置。
- 前記転がり軸受の保持器は、外周面が軸方向外側に向かって大径となる傾斜面を有する、請求項1~6のいずれか1項に記載の軸受装置。
- 前記潤滑剤はグリースである、請求項1~7のいずれか1項に記載の軸受装置。
- スピンドルが、請求項1~8のいずれか1項に記載の軸受装置によって回転自在に支持された工作機械主軸用スピンドル装置。
- スピンドルが、請求項1~8のいずれか1項に記載の軸受装置によって回転自在に支持された高速モータ用スピンドル装置。
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JP2015113956A (ja) * | 2013-12-13 | 2015-06-22 | 日本精工株式会社 | 軸受装置及びスピンドル装置 |
JP2021014410A (ja) | 2019-07-10 | 2021-02-12 | ダイキン工業株式会社 | ビニル化合物の製造方法 |
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