WO2013002252A1 - 転がり軸受 - Google Patents
転がり軸受 Download PDFInfo
- Publication number
- WO2013002252A1 WO2013002252A1 PCT/JP2012/066366 JP2012066366W WO2013002252A1 WO 2013002252 A1 WO2013002252 A1 WO 2013002252A1 JP 2012066366 W JP2012066366 W JP 2012066366W WO 2013002252 A1 WO2013002252 A1 WO 2013002252A1
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- WIPO (PCT)
- Prior art keywords
- rolling
- outer ring
- rolling bearing
- bearing
- cage
- Prior art date
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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
- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—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
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
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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
- 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
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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
- 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
- F16C33/6685—Details of collecting or draining, e.g. returning the liquid to a sump
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
- F16C33/7806—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for spherical roller bearings
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—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
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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
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
Definitions
- This invention relates to a rolling bearing used for supporting, for example, a machine tool spindle.
- FIG. 16 is a longitudinal sectional view of a conventional rolling bearing with a nozzle spacer.
- exhaust notches 71 and 71 are provided in the spacer 70, and the lubricant used for lubricating the bearing is discharged from the exhaust notches 71 and 71 to the outside of the bearing.
- Patent Document 1 there is a system in which an oil supply hole that communicates from an outer diameter portion to an inner diameter portion is provided in an outer ring, and oil is supplied from the oil supply hole.
- An object of the present invention is to provide a rolling bearing capable of smoothly discharging the air oil supplied into the bearing space to the outside of the bearing when a bearing having an oil supply hole in the outer ring is used without a spacer. That is.
- a rolling bearing according to the present invention is a rolling bearing in which rolling elements are interposed between rolling surfaces of an inner ring and an outer ring, and the outer ring is provided with an oil supply hole for air oil lubrication penetrating into a bearing space.
- One or both of the width surfaces are provided with notch recesses for exhausting air oil that are recessed inward in the axial direction of the bearing from the inner diameter surface to the outer diameter surface.
- a circumferential groove communicating with the oil supply hole is provided on the outer diameter surface of the outer ring, and annular grooves are provided on both sides of the circumferential groove on the outer diameter surface of the outer ring.
- a seal member may be provided. These annular seal members can prevent air oil from undesirably leaking from the outer diameter surface of the outer ring.
- the circumferential phase of the notch recesses of each bearing may be arranged in the same phase.
- a large discharge area that is, a cross-sectional area of the notch recess can be secured.
- the air oil used for lubrication in each bearing is quickly discharged from the notched recess without almost moving into the bearing space of the adjacent bearing. In this way, an effective exhaust and drainage flow can be realized for the air oil. Therefore, the unstable displacement of the bearing temperature can be reliably eliminated.
- the inner diameter surface of the outer ring may be formed in a cross-sectional shape that is inclined so that the diameter dimension increases from the rolling surface side toward the width surface side.
- the air oil that has been lubricated in the bearing space moves from the inner ring side to the outer ring side due to the centrifugal force generated by the rotation of the inner ring and the exhaust and oil discharge flow accompanying this centrifugal force.
- a part of the air oil may stay on the inner diameter surface of the outer ring.
- the inner diameter surface of the outer ring is inclined as described above, the air oil does not stay on the inner diameter surface of the outer ring. It is discharged smoothly.
- a counter bore portion may be formed on the outer diameter surface of the inner ring, and a protruding portion protruding toward the outer diameter side may be provided at an axial end portion of the counter bore portion.
- a counterbore portion is formed on one of the outer diameter surfaces of the inner ring, and an anti-counterbore portion without a counterbore portion is formed on the other, and the anti-counterbore portion is formed from the rolling surface side of the inner ring.
- You may form in the cross-sectional shape which inclines so that a radial dimension may become large as it goes to the width surface side.
- the air oil present in the counter-counter bore portion flows along the width surface side from the rolling surface side in the inclined surface of the counter-counter bore portion, and moves toward the notch recess. Therefore, an effective exhaust and exhaust oil flow can be realized.
- a counter bore portion may be formed on the outer diameter surface of the inner ring, and when a plurality of rolling bearings are combined, an annular member having a diameter larger than the inner ring counter diameter of the counter bore portion may be sandwiched between the bearings.
- the annular member may have a thin plate shape of, for example, a few millimeters or less.
- the circumferential phase of the notch recess of the outer ring and the oil supply hole may be arranged in the same phase.
- the distance between the supply and discharge oil in the bearing can be made smaller than that obtained by making the circumferential phase of the notch recess and the oil supply hole different from each other, and a more effective exhaust and oil discharge flow can be obtained. be able to.
- the cross-sectional area of the exhaust outlet can be made larger than the cross-sectional area of the exhaust inlet, and a more effective exhaust and exhaust oil flow can be obtained.
- the rolling bearing may be an angular ball bearing. It has a cage that holds a plurality of rolling elements at regular intervals in the circumferential direction, and this cage may be an outer ring guide type or a rolling element guide type.
- this cage can be prevented from swinging during high-speed rotation by making the cage an outer ring guide type.
- the cage is a rolling element guide type, and the outer diameter surface of the cage is formed in a cross-sectional shape that is inclined so that the diameter dimension increases from the pocket side holding the rolling element toward the cage end surface side. May be.
- the air oil existing in the vicinity of the outer diameter surface of the cage flows from the small diameter side to the large diameter side of the inclined surface and smoothly moves toward the notch recess.
- the rolling bearing may be a cylindrical roller bearing with an inner ring collar. It has a cage that holds a plurality of rolling elements at regular intervals in the circumferential direction, and this cage may be an outer ring guide type or a rolling element guide type.
- the main spindle for machine tools according to the present invention uses a rolling bearing according to any one of the above-described configurations. In this case, the spindle speed can be increased and the temperature rise can be reduced.
- (A) is a longitudinal cross-sectional view of a rolling bearing according to an eighth embodiment of the present invention, and (B) is a plan view of the bearing as viewed from the direction of arrow A in FIG. 11 (A).
- (A) is one side view of the outer ring
- (B) is the other side view of the outer ring
- (A) is a longitudinal sectional view of a rolling bearing according to a tenth embodiment of the present invention, and (B) is a plan view of the same bearing as viewed from the direction of arrow A in FIG.
- (A) is a longitudinal cross-sectional view of a rolling bearing according to an eleventh embodiment of the present invention
- (B) is a plan view of the bearing as viewed from the direction of arrow A in FIG. 14 (A).
- It is a longitudinal cross-sectional view of the main axis for machine tools using the rolling bearing which concerns on any embodiment of this invention.
- It is a longitudinal cross-sectional view of the rolling bearing with a nozzle spacer of a prior art example.
- It is a longitudinal cross-sectional view of the rolling bearing of another conventional example.
- the rolling bearing according to this embodiment is used for supporting a machine tool spindle, for example, and is used in air-oil lubrication. However, it is not limited to machine tool spindle applications.
- the rolling bearing includes an inner ring 1, an outer ring 2, and a plurality of rolling elements 3 interposed between the rolling surfaces 1a and 2a of the inner and outer rings 1 and 2.
- the rolling bearing of this example is an angular ball bearing, and the rolling element 3 is made of a ball.
- Each rolling element 3 is held in a pocket 4a of a ring-shaped cage 4 at regular intervals in the circumferential direction.
- As the cage 4 for example, an outer ring guide type guided by the inner diameter surface 2 b of the outer ring 2 is applied.
- FIG. 1 (B) is a plan view seen from the direction of arrow A in FIG. 1 (A).
- the outer ring 2 is provided with an oil supply hole 5 and a circumferential groove 6 for air oil lubrication.
- the oil supply hole 5 is a through hole that communicates the outer diameter surface 2c of the outer ring 2 and the position in the vicinity of the rolling surface of the outer ring inner diameter surface 2b in the radial direction, and is a hole that supplies air oil into the bearing space.
- the position in the vicinity of the rolling surface refers to the side of the outer ring inner diameter surface 2b on the opposite side of the rolling element 3 and the outer ring 2 from the center of the rolling element until air oil discharged from the oil supply hole 5 is applied to the rolling element 3.
- the “non-contact side” refers to a side of the outer ring 2 opposite to the biased side of the action line L1 that forms a contact angle with the rolling surface 2a.
- the oil supply holes 5 are provided at two positions at 180 ° diagonal positions in the outer ring 2.
- a circumferential groove 6 is provided on the outer diameter surface 2c of the outer ring 2, and the circumferential groove 6 communicates with the two oil supply holes 5 and 5, respectively.
- the outer circumferential surface 2c of the outer ring 2 is provided so that the circumferential groove 6 passes through a portion where the opening ends of the two oil supply holes 5 and 5 are located.
- the circumferential groove 6 is formed in an arc-shaped cross section, and for example, is arranged so that the groove bottom position of the circumferential groove 6 matches the central axis of the oil supply holes 5 and 5. It is installed. Moreover, in this example, it is provided in the circumferential groove
- annular grooves 7 and 7 are provided at positions on both sides of the circumferential groove 6 on the outer diameter surface 2c of the outer ring 2, respectively.
- the annular grooves 7 and 7 are provided with annular seal members 8 and 8 each composed of an O-ring. That is, by providing the annular seal members 8 and 8 on both sides of the circumferential groove 6 and the oil supply holes 5 and 5 between the inner peripheral surface of the housing Hs and the outer diameter surface 2c of the outer ring 2, air oil To prevent leakage.
- Notch recesses 9 and 9 for exhausting air oil are provided on both width surfaces of the outer ring 2. As shown in FIGS. 2A and 2B, the notch recesses 9 and 9 on both width surfaces of the outer ring 2 have the same phase and the same shape, and therefore only the notch recesses 9 and 9 on one width surface.
- the notch recesses 9 and 9 on the other width surface will be described with the same reference numerals and will not be described in detail.
- the “width surface” may be referred to as an “end surface”.
- the notch recesses 9 and 9 on the one width surface are respectively recessed inward in the axial direction of the bearing, and provided from the inner diameter surface 2b to the outer diameter surface 2c of the outer ring 2. Yes.
- the notch recesses 9 and 9 are disposed at 180 ° diagonal positions of the outer ring 2, and the notch recesses 9 and 9 have the same width dimensions H1 and H1. It is provided to become.
- the notch recesses 9 and 9 are formed in a concave cross-sectional shape in which the bottom depths D1 and D1 (FIG. 1B) are the same depth.
- the notched recesses 9 and 9 of the outer ring 2 are provided with a predetermined angle ⁇ 1 with respect to the phases of the oil supply holes 5 and 5.
- FIG. 3 is a longitudinal sectional view showing an example in which two rolling bearings are combined with the back surface (DB combination) without a spacer.
- the circumferential phases of the notch recesses 9 and 9 of each bearing are arranged in the same phase.
- a comparison test was performed for the presence or absence of the notched recess 9 when the two rolling bearings were combined with the back without a spacer.
- the number of rotations of the bearing is increased step by step with the passage of a predetermined operating time. The relationship between bearing temperature and operation time was compared.
- Fig. 4 (A) shows test data of a combination bearing with a notched recess, which is an actual product
- Fig. 4 (B) shows test data of a combination bearing without a notch, which is a comparative product.
- the cut-out recesses 9 of the product used for the test were provided on both width surfaces of the outer ring 2. Further, two notches 9 and 9 are provided at 180 ° diagonal positions for each width surface.
- the size of the notch recess 9 is a bearing having an inner diameter of ⁇ 100 mm, a width of 30 mm, and a depth of 2 mm. According to the test results, in the comparative product without a notch recess shown in FIG.
- FIGS. 5 to 14A and 14B second to eleventh embodiments of the present invention will be described with reference to FIGS. 5 to 14A and 14B.
- the same or corresponding parts as those in the first embodiment shown in FIGS. 1 (A) and (B) are the same. A detailed description thereof is omitted with reference numerals.
- the rolling bearings may be combined on the back surface, and the inner diameter surface 2b of the outer ring 2 may be formed in a cross-sectional shape that is inclined so that the diameter dimension increases from the rolling surface side toward the width surface side.
- the air oil that has been lubricated in the bearing space moves from the inner ring 1 side to the outer ring 2 side due to the centrifugal force generated by the rotation of the inner ring, the exhaust gas accompanying the centrifugal force, and the oil flow.
- a part of the air oil may stay on the inner diameter surface 2b of the outer ring 2, but the air oil does not stay on the inner diameter surface 2b of the outer ring 2 because the inner diameter surface 2b of the outer ring 2 is inclined as described above.
- the liquid is smoothly discharged along the inclined surface 2b.
- the rolling bearing having the counter bore portion 10 formed on the outer diameter surface of the inner ring 1 is combined with the back surface, and the axial end portion of the counter bore portion 10 has an outer diameter side.
- the air oil existing in the vicinity of the protruding portion 11 flows from the inner diameter side portion of the protruding portion 11 along the outer diameter side portion toward the notch recess 9 during the bearing operation. Therefore, an effective exhaust and exhaust oil flow can be realized.
- a rolling bearing in which the counter bore portion 10 is formed on the back side and the counter counter bore portion 12 is formed on the front side of the outer diameter surface of the inner ring 1 is combined with the back surface.
- the counter-bore portion 12 may be formed in a cross-sectional shape that inclines so that the diameter dimension increases from the rolling surface 1a side of the inner ring 1 toward the width surface side.
- the air oil existing in the counter-counter bore portion 12 flows along the width surface side from the rolling surface 1a side of the inclined surface of the counter-counter bore portion 12 toward the notch recess 9. Therefore, an effective exhaust and exhaust oil flow can be realized.
- annular member 13 having a diameter larger than the inner ring counter diameter D ⁇ b> 2 of the inner ring counter bore portion 10 is sandwiched between the inner ring end faces. It is good as a thing.
- the annular member 13 is made of a thin steel plate or the like.
- the inner diameter of the annular member 13 is substantially the same as the inner ring inner diameter, and the outer diameter of the annular member 13 is larger than the inner ring counter diameter D2 and smaller than the inner diameter of the outer ring. It has been established.
- An annular member 14 made of a thin steel plate or the like is sandwiched between the outer ring end faces.
- the annular member 14 has the same thickness as the annular member 13 between the inner ring end faces, is larger in diameter than the inner diameter of the outer ring, and is substantially the same as the outer diameter of the outer ring. According to this configuration, by sandwiching the annular member 13 having a diameter larger than the inner ring counter diameter D2 between the end surfaces of the inner ring, air oil used for lubrication in each bearing is blocked by the annular member 13 and adjacent thereto. It is quickly discharged from the notch recess 9 with little movement into the bearing space of the bearing.
- the cage 4A of each bearing is an outer ring guide type, and the inner diameter surface 4Aa of the cage 4A is held from the pocket 4a side. It is formed in a cross-sectional shape that inclines so that the diameter dimension increases toward the end face of the vessel.
- the air oil existing in the vicinity of the inner diameter surface of the cage 4 ⁇ / b> A flows along the larger diameter side from the smaller diameter side of the cage inclined surface during the bearing operation, and smoothly moves toward the notch recess 9.
- the cage 4B of each bearing is a rolling element guide type, and the outer diameter surface 4Bb of this cage 4B is connected to the pocket 4a side. It is formed in the cross-sectional shape which inclines so that a radial dimension may become large as it goes to a cage end surface side.
- the inner diameter surface 4Ba of the cage 4B is also an inclined surface parallel to the outer diameter surface 4Bb.
- the circumferential phase of the notch recess 9 and the oil supply hole 5 of the outer ring 2 may be arranged in the same phase.
- the distance between the oil supply and discharge oil in the bearing can be made smaller than in the embodiment shown in FIG. 12B in which the circumferential phase of the notch recess 9 and the oil supply hole 5 is different by 90 degrees. Effective exhaust and drainage flow can be achieved.
- the outer circumferential surface 2c of the outer ring 2 has no circumferential groove, and as shown in FIG. 13B, the oil supply hole 5 in the outer diameter surface 2c is formed.
- An annular groove 16 may be provided in the outer peripheral portion of the exhaust outlet.
- the annular groove 16 is provided with an annular seal member 8A made of an O-ring for preventing air oil leakage. In this case, the number of processing steps can be reduced and the number of parts can be reduced as compared with the case where the two circumferential grooves 6 and 6 are formed.
- the rolling bearing may be a cylindrical roller bearing with an inner ring collar.
- the axial position of the oil supply hole 5 in the outer ring 2 is provided so as to match the one end surface 3 a of the rolling element 3.
- the air oil can be reliably guided to the cage pocket 4a and the collar surface 1c of the inner ring 1, and the lubrication effect can be enhanced.
- the same operational effects as the above-described embodiments are obtained.
- the outer ring guide type cage may be changed to a rolling element guide type cage, and conversely, the rolling element guide type cage may be changed to an outer ring guide type.
- FIG. 15 is a longitudinal sectional view of a main spindle for a machine tool using the rolling bearing according to any one of the above embodiments.
- the example of FIG. 15 is a so-called built-in motor driven spindle for a machine tool in which a motor is built in a housing.
- a rotor 19 of a motor 18 is attached to the main shaft 17, and a stator 20 of the motor 18 is attached to the housing Hs.
- the rotor 19 is made of a permanent magnet or the like
- the stator 20 is made of a coil, a core, or the like.
- the cylindrical roller bearing BR1 according to the embodiment and the angular ball bearing BR2 combined with the back surface are arranged on the front end side of the main shaft 17, and the cylindrical roller bearing BR1 according to the embodiment is also arranged on the rear end side of the main shaft 17.
- each bearing BR1, BR2 is fitted to the outer circumferential surface of the main shaft 17, and the outer ring 2 is fitted to the inner circumferential surface of the housing Hs.
- These inner and outer rings 1 and 2 are fixed to the main shaft 17 and the housing Hs by an inner ring presser 21 and an outer ring presser 22, respectively.
- An air oil supply path 23 is provided in the housing Hs, and the air oil supply path 23 is connected to an air oil supply source (not shown).
- the air oil supply path 23 communicates with the oil supply hole 5 of each outer ring 2.
- the housing Hs is provided with an air oil exhaust groove 24 communicating with the notched recess 9 of each outer ring 2 and an air oil exhaust passage 25 connected to each air oil exhaust groove 24.
- Air oil is exhausted from the air oil exhaust passage 25.
- the main shaft 17 can be shortened and the main shaft rigidity can be increased as compared with the conventional case where the spacer is provided between the bearings. it can.
- it is possible to prevent the bearing temperature from being unstablely displaced or to raise the temperature excessively, so that the speed and accuracy of the main shaft 17 can be increased.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Turning (AREA)
- Sealing Of Bearings (AREA)
Abstract
Description
2…外輪
1a,2a…転走面
2b…内径面
2c…外径面
3…転動体
5…給油孔
6…円周溝
7…環状溝
8,8A…シール部材
10…カウンタボア部
11…突出部
12…反カウンタボア部
13…環状部材
15…面取り
Claims (15)
- 内輪および外輪の転走面間に転動体を介在させた転がり軸受であって、
前記外輪に、軸受空間内に貫通するエアオイル潤滑用の給油孔を設け、前記外輪の幅面のうちいずれか一方または両方に、軸受の軸方向内方に凹むエアオイル排気用の切欠き凹部を、内径面から外径面にわたって設けた転がり軸受。 - 請求項1において、前記外輪の外径面に、給油孔に連通する円周溝を設けると共に、この外輪の外径面における、前記円周溝の両側位置に、それぞれ環状溝を設け、各環状溝にそれぞれ環状のシール部材を設けた転がり軸受。
- 請求項1において、複数の転がり軸受の組合せ時に、各軸受の切欠き凹部の円周方向の位相を同位相に配置した転がり軸受。
- 請求項1において、前記外輪の内径面を、転走面側から幅面側に向かうに従って径寸法が大きくなるように傾斜する断面形状に形成した転がり軸受。
- 請求項1において、前記内輪の外径面に、カウンタボア部が形成され、このカウンタボア部における軸方向端部に、外径側に突出する突出部を設けた転がり軸受。
- 請求項1において、前記内輪の外径面のうちいずれか一方にカウンタボア部が形成され、他方に、カウンタボア部の無い反カウンタボア部が形成され、この反カウンタボア部を、前記内輪の転走面側から幅面側に向かうに従って径寸法が大きくなるように傾斜する断面形状に形成した転がり軸受。
- 請求項1において、前記内輪の外径面に、カウンタボア部が形成され、複数の転がり軸受の組合せ時に、カウンタボア部の内輪カウンタ径よりも大径となる環状部材を軸受間に挟み込んで設けた転がり軸受。
- 請求項1において、前記外輪の切欠き凹部と給油孔との円周方向の位相を同位相に配置した転がり軸受。
- 請求項1において、前記外輪の切欠き凹部と、この外輪の外径面との角部に、面取りを設けた転がり軸受。
- 請求項1において、前記転がり軸受がアンギュラ玉軸受である転がり軸受。
- 請求項10において、複数の転動体を円周方向一定間隔おきに保持する保持器を有し、この保持器を外輪案内形式または転動体案内形式とした転がり軸受。
- 請求項11において、前記保持器が転動体案内形式であって、この保持器の外径面を、転動体を保持するポケット側から保持器端面側に向かうに従って径寸法が大きくなるように傾斜する断面形状に形成した転がり軸受。
- 請求項1において、前記転がり軸受が内輪つば付の円筒ころ軸受である転がり軸受。
- 請求項13において、複数の転動体を円周方向一定間隔おきに保持する保持器を有し、この保持器を外輪案内形式または転動体案内形式とした転がり軸受。
- 請求項1の転がり軸受を用いた工作機械用主軸。
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CN201280030846.9A CN103635708B (zh) | 2011-06-30 | 2012-06-27 | 滚动轴承 |
KR1020137033508A KR101968714B1 (ko) | 2011-06-30 | 2012-06-27 | 롤링 베어링 |
DE112012002734.5T DE112012002734B4 (de) | 2011-06-30 | 2012-06-27 | Wälzlagereinrichtung, kombinierte Wälzlagereinheit und Werkzeugmaschinenhauptwelle |
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JP2011146142A JP5917030B2 (ja) | 2011-06-30 | 2011-06-30 | 転がり軸受 |
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WO2018181524A1 (ja) * | 2017-03-30 | 2018-10-04 | Ntn株式会社 | 転がり軸受用保持器および外輪給油孔付き転がり軸受 |
US10415646B2 (en) * | 2016-09-16 | 2019-09-17 | Steering Solutions Ip Holding Corporation | Telescoping roller I-shaft and method of assembly |
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JP6439469B2 (ja) * | 2015-02-04 | 2018-12-19 | 日本精工株式会社 | 転がり軸受 |
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JP2013015152A (ja) | 2013-01-24 |
CN105605101B (zh) | 2020-12-11 |
DE112012002734B4 (de) | 2022-12-22 |
DE112012002734T5 (de) | 2014-04-03 |
CN103635708A (zh) | 2014-03-12 |
CN103635708B (zh) | 2017-04-19 |
KR101968714B1 (ko) | 2019-04-12 |
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