WO2013042552A1 - 転がり軸受装置 - Google Patents

転がり軸受装置 Download PDF

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Publication number
WO2013042552A1
WO2013042552A1 PCT/JP2012/072853 JP2012072853W WO2013042552A1 WO 2013042552 A1 WO2013042552 A1 WO 2013042552A1 JP 2012072853 W JP2012072853 W JP 2012072853W WO 2013042552 A1 WO2013042552 A1 WO 2013042552A1
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WO
WIPO (PCT)
Prior art keywords
oil
bearing
inner ring
lubricating oil
spacer
Prior art date
Application number
PCT/JP2012/072853
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
恩田裕士
林康由
水谷守
玉田健治
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2011207723A external-priority patent/JP5739293B2/ja
Priority claimed from JP2011250448A external-priority patent/JP5816061B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2013042552A1 publication Critical patent/WO2013042552A1/ja

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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
    • 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
    • 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
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators

Definitions

  • the present invention relates to a rolling bearing device that rotatably supports a machine tool main shaft, for example, and relates to a rolling bearing provided with a supply / discharge oil mechanism that supplies lubricating oil also serving as a bearing cooling medium into the bearing and discharges it outside the bearing. Relates to the device.
  • a lubricating device having a mechanism for cooling a bearing and supplying and discharging lubricating oil to and from the bearing has been proposed (Patent Document 1).
  • this lubricating device as shown in FIG. 40 (A), an inner ring spacer 50 in contact with the inner ring end face is provided, and a lubricating oil introducing member 51 in contact with the outer ring end face is provided.
  • a circumferential groove 53 is provided on the slope of the inner ring 52 from the inner ring end face to the inner ring raceway surface, a nozzle 54 is provided in the lubricating oil introduction member 51, and a bearing cooling medium is provided from the nozzle 54 into the circumferential groove 53. It is designed to discharge lubricating oil.
  • FIG. 40 (A) an inner ring spacer 50 in contact with the inner ring end face is provided, and a lubricating oil introducing member 51 in contact with the outer ring end face is provided.
  • a circumferential groove 53 is provided on the slope of the inner
  • the arrow indicates the flow of the lubricating oil.
  • the inner ring 52 is cooled by discharging the lubricating oil introduced into the lubricating oil introducing member 51 into the circumferential groove 53. A part of the lubricating oil in the circumferential groove 53 is supplied into the bearing from the gap between the cover portion 55 extending from the lubricating oil introduction member 51 into the bearing and the inclined surface.
  • the present applicant has proposed a rolling bearing device shown in FIG.
  • the inner ring 1 is provided with an inner ring extension portion 6 that extends in the axial direction, and an outer ring spacer 7 that is adjacent to the outer ring 2 and whose inner peripheral surface faces the inner ring extension portion 6.
  • the lubricating oil enters the bearing as shown in (1) to (5) below.
  • the arrows in the figure indicate the flow of the lubricating oil.
  • the lubricating oil hits the inner ring circumferential groove 8.
  • the lubricating oil receives centrifugal force from the rotating inner ring 1 and hits the inner peripheral surface 7 a of the outer ring spacer 7.
  • Lubricating oil enters the bearing from the radial clearance between the outer peripheral surface of the inner ring extension 6 and the inner peripheral surface of the outer ring spacer 7. At this time, when the rolling bearing device is used for supporting the vertical shaft, for example, the lubricating oil hitting the inner peripheral surface 7a is discharged too much at the oil discharge port due to the action of gravity or the like in the course of going to the oil discharge port. In some cases, a large amount may enter the bearing. (5) When a large amount of lubricating oil enters in this way, the lubricating oil stays in the bearing. This accumulated lubricating oil causes heat generation of the bearing, and high speed operation becomes impossible.
  • FIG. 42 is a longitudinal sectional view schematically showing an image in which lubricating oil stays in the bearing
  • FIG. 43 is a plan view of an outer ring spacer of the bearing.
  • the present applicant arranges a plurality of rolling bearings arranged in the axial direction, and each rolling bearing is provided with an inner ring extension 56 extending in the axial direction on the inner ring, adjacent to the outer ring and on the inner circumference.
  • a lubrication device for a rolling bearing has been proposed in which an outer ring spacer 57 whose surface faces the inner ring extension 56 is provided, and an oil supply / discharge oil mechanism is provided between the inner ring extension 56 and the outer ring spacer 57.
  • the supply / discharge oil mechanism is a mechanism that supplies lubricating oil that also serves as a bearing cooling medium to the bearing space in each rolling bearing and discharges it to the outside of the bearing.
  • An object of the present invention is to provide a rolling bearing that enables high-speed operation by preventing lubricating oil that has entered the bearing from being smoothly drained to the outside of the bearing to prevent an increase in stirring resistance and suppressing a rise in temperature inside the bearing. It is to provide a lubrication device.
  • the rolling bearing device supplies a rolling bearing in which a plurality of rolling elements held by a cage are interposed between raceway surfaces of inner and outer rings, and lubricating oil serving as a bearing cooling medium to a bearing space in the bearing.
  • a rolling bearing device having a supply and discharge oil mechanism for discharging outside the bearing the inner ring is provided with an inner ring extension extending in the axial direction, and the inner ring is adjacent to the outer ring and the inner circumferential surface is provided in the inner ring extension.
  • Opposing outer ring spacers are provided, and the oil supply / discharge oil mechanism is provided in an inner ring circumferential groove provided on the outer circumferential surface of the inner ring extension, and in the outer ring spacer, and lubricating oil is directed toward the inner ring circumferential groove.
  • an oil supply passage having an oil supply port for discharging, an outer peripheral surface formed on the bearing side of an inner ring circumferential groove in an outer peripheral surface of the inner ring extension, and an inner peripheral surface of the outer ring spacer; A radial clearance for guiding the lubricating oil into the bearing and the outer ring spacer, And an oil discharge port that discharges lubricating oil at a circumferential position different from the port, and is provided on an inner peripheral surface of the outer ring spacer.
  • Opposite spacers disposed adjacent to the end face of the inner and outer rings on the opposite side of the inner ring extension from the recess that collects the lubricating oil that is supplied from the oil supply port and bounces back at the inner ring circumferential groove.
  • the “inner ring extension” refers to a portion of the inner ring that extends in the axial direction with respect to a portion that satisfies the required strength as a bearing.
  • the lubricating oil flows along the inner ring circumferential groove on the outer peripheral surface of the inner ring extension. This cools the bearing.
  • the oil that has cooled the bearing is discharged from the oil outlet of the outer ring spacer.
  • the lubricating oil supplied from the oil supply passage and bounced off by the inner ring circumferential groove is collected in the recess of the inner peripheral surface of the outer ring spacer, and the intrusion of the lubricating oil into the bearing is suppressed.
  • the lubricating oil collected in the recess is smoothly discharged toward the oil discharge port.
  • an appropriate amount of lubricating oil for lubricating the bearing is supplied into the bearing through the radial clearance, and then discharged out of the bearing.
  • the lubricating oil bounced off by the inner ring circumferential groove can be collected in the recess provided on the inner peripheral surface of the outer ring spacer and smoothly discharged, so that a large amount of lubricating oil is prevented from entering the bearing. Can do. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.
  • the lubricating oil introduced into the bearing by the oil supply / discharge oil mechanism cools the bearing and is discharged outside the bearing.
  • a part of the introduced lubricating oil is supplied to the bearing space in the rolling bearing for lubrication.
  • Part of the lubricating oil used for lubrication of the rolling bearing flows along the oil groove on the end face of the other spacer in the rolling bearing disposed adjacent to the rolling bearing, and is discharged outside the bearing.
  • the recess may be a circumferential groove provided on the inner peripheral surface of the outer ring spacer.
  • the lubricating oil flows along the circumferential groove, and this lubricating oil can be smoothly discharged from the oil discharge port.
  • the axial position of the opening peripheral part connected to the radial clearance and the axial position of the opening peripheral part connected to the radial clearance of the inner ring circumferential groove are matched, and the recess and the inner ring
  • the width dimension of the circumferential groove may be the same.
  • Lubricating oil existing in the inner ring circumferential groove receives centrifugal force from the rotating inner ring and advances toward the outer ring spacer.
  • the lubricating oil passes through the upper portion of the radial clearance by matching the axial positions of the opening peripheral edge of the recess and the opening peripheral edge of the inner ring circumferential groove. For this reason, it becomes difficult for the lubricating oil to enter the bearing, and the lubricating oil that has passed through the upper portion of the radial clearance goes to the oil outlet. Furthermore, by making the width of the recess and the inner ring circumferential groove the same, the lubricating oil present in the inner ring circumferential groove is reliably collected in the recess by centrifugal force from the inner ring, and the lubricant is not desired from the recess. Can be prevented from overflowing. Therefore, it is possible to prevent the lubricating oil from being undesirably discharged from locations other than the oil discharge port.
  • the recess may be narrower toward the bottom surface.
  • the lubricating oil hits the inner ring circumferential groove and is rebounded by the centrifugal force accompanying the inner ring rotation.
  • the rebounded lubricating oil travels toward the oil discharge port along a groove having a narrow recessed portion, in other words, a wedge-shaped groove.
  • the lubricating oil is discharged from the oil discharge port. Since the lubricating oil is directed to the oil discharge port along the groove that becomes narrower in the recessed portion, the lubricating oil bounced back against the inner ring circumferential groove can be efficiently collected in the recessed portion.
  • the recessed portion has a circumferential groove provided on the inner circumferential surface of the outer ring spacer, and a circumferential groove connected to a lower portion of the circumferential groove and having a width dimension larger than that of the circumferential groove. Also good. In this case, the lubricating oil bounced off against the inner ring circumferential groove can be collected in the circumferential groove having the large width dimension and smoothly drained.
  • the oil drain port of the outer ring spacer may be provided in a tangential direction connected to the circumferential groove of the outer ring spacer.
  • the lubricating oil supplied from the oil filler opening of the outer ring spacer bounces back against the inner ring circumferential groove, flows along the circumferential groove of the outer ring spacer, and is smoothly discharged without staying at the oil outlet. .
  • the recess may be provided in an arc shape extending from the oil supply port of the outer ring spacer to the oil discharge port. In this case, the lubricating oil flowing through the recessed portion of the outer ring spacer is blocked by the oil discharge port. The blocked lubricating oil is quickly discharged from the oil discharge port.
  • the inner ring circumferential groove may have oil repellency.
  • the lubricating oil existing in the inner ring circumferential groove can be easily directed to the recessed portion of the outer ring spacer, and smooth draining can be performed.
  • the lubricating oil introduced into the bearing from the radial clearance can be reliably and appropriately guided to the inner ring raceway surface via the slope of the inner ring by the centrifugal force generated by the inner ring rotation.
  • the oil groove is a virtual cylinder including an outer ring inner circumferential surface, a rolling element outer circumferential surface, and a cage outer circumferential surface on the opposite side to the inner ring extension in the cross section including the shaft center and the rolling element center in the rolling bearing. It may have a cross-sectional area larger than the cross-sectional area formed by the surface and the end surface of the other spacer. In this case, it is possible to prevent a certain amount of lubricating oil from accumulating in the oil groove and to retain the lubricating oil inside the bearing.
  • a discharge port communicating with the oil groove and discharging the lubricating oil in the oil groove to the outside of the bearing may be provided.
  • Part of the lubricating oil used for the lubrication of the rolling bearing flows along the oil groove on the end face of the other spacer in the adjacent rolling bearing, and is discharged from the oil groove to the outside through the discharge port.
  • the discharge port may have a depth dimension larger than the depth dimension of the oil groove. In this case, the lubricating oil flowing through the oil groove easily flows to the discharge port due to the action of gravity, and the lubricating oil can be smoothly discharged from the discharge port to the outside of the bearing.
  • a notch penetrating in the bearing radial direction may be provided in a part of the circumferential direction on the end face of the outer ring adjacent to the other spacer.
  • the other spacer is provided with a discharge port that communicates with the oil groove and discharges the lubricating oil in the oil groove to the outside of the bearing, and among the other spacers, the intersection where the oil groove and the discharge port communicate with each other
  • a wall portion that restricts the flow of the lubricating oil along the oil groove may be provided.
  • the lubricating oil that has flowed into the oil groove from the bearing space flows in the rotational direction of the bearing.
  • the wall portion may be disposed at the central portion of the circumferential length of the outlet of another spacer. Even when the bearing rotates in the reverse direction, the lubricating oil flowing in the reverse rotation direction along the oil groove can be regulated by the wall portion and smoothly guided to the discharge port.
  • Any of the rolling bearing lubrication devices may be used for supporting the spindle of a machine tool.
  • FIG. 1 is a longitudinal sectional view of a rolling bearing device according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the principal part which shows the example of a shape of the outer ring
  • (A) is a top view which shows the flow of the lubricating oil in the rolling bearing apparatus
  • (B) is a front view of the principal part of FIG. 4 (A).
  • FIG. 6 is a longitudinal sectional view showing an example in which the rolling bearing device according to the first to sixth embodiments of the present invention is applied to a rolling bearing that supports a machine tool main shaft.
  • FIG. 17 is a cross-sectional view taken along the line XI-XI of FIG. 16, showing the main part of a rolling bearing lubrication device according to a seventh embodiment of the present invention. It is a principal part enlarged view of FIG. It is a longitudinal cross-sectional view which shows the oil supply / discharge oil mechanism of the lubricating device of the rolling bearing. It is an expanded sectional view of the principal part of the supply and discharge oil mechanism.
  • FIG. 17 is a cross-sectional view taken along the line XVIII-XVIII in FIG. 16, showing the main part of the lubrication device for the rolling bearing.
  • FIG. 1 It is a top view which shows the flow of the lubricating oil in the rolling bearing apparatus.
  • (A) is a top view of the principal part of the rolling bearing apparatus which concerns on other embodiment of this invention
  • (B) is the XXVI-XXVI line end view of the same figure (A). It is a top view of the principal part of the rolling bearing apparatus which concerns on the application form 2 of this invention. It is a top view of the principal part of the rolling bearing apparatus which concerns on the application form 3 of this invention. It is a top view of the principal part of the rolling bearing apparatus which concerns on the application form 4 of this invention.
  • (A) is a rolling bearing device according to Application Mode 5 of the present invention, and is a plan view of the main part showing a state when the inner ring rotates counterclockwise in the figure, and (B) is the same in the inner ring. It is a top view of the principal part showing a state when rotating clockwise. It is a perspective view of the outer ring
  • the rolling bearing device includes a rolling bearing BR and a supply / discharge oil mechanism KU.
  • the rolling bearing BR includes a pair of bearing rings that are inner and outer rings 1 and 2, a plurality of rolling elements 3 interposed between the raceway surfaces 1 a and 2 a of the inner and outer rings 1 and 2, and these rolling elements.
  • a ring-shaped cage 4 that holds 3.
  • the rolling bearing is an angular ball bearing, and a ball made of a steel ball, a ceramic ball or the like is applied as the rolling element 3.
  • the inner ring 1 has an inner ring main body 5 and an inner ring extension 6 extending integrally from the inner ring main body 5.
  • the inner ring extension 6 extends in the width direction from the biased side of the action line L that forms a contact angle with the raceway surface 1 a of the inner ring main body 5.
  • the inner ring main body 5 satisfies the necessary strength as a bearing, and has the same width as the outer ring 2 and is provided with a predetermined width.
  • the predetermined width dimension is a width dimension of the inner ring defined in JIS, a bearing catalog or the like.
  • a raceway surface 1 a is formed at the center of the outer peripheral surface of the inner ring main body 5.
  • 1b (FIG. 2) is formed, and a flat outer diameter surface 1c is formed on the other side in the axial direction connected to the track surface 1a of the outer peripheral surface.
  • An inner ring extension 6 is integrally provided on the inner ring back side (bearing front side) of the inner ring main body 5 so as to extend in one axial direction.
  • the outer ring inner diameter surface 2b and the counter bore 2c are formed on both axial sides of the raceway surface 2a of the outer ring 2, respectively.
  • the cage 4 is configured to be guided to the outer ring inner surface 2b.
  • the oil supply / discharge mechanism KU is a mechanism that supplies lubricating oil that also serves as a bearing cooling medium into the bearing and discharges it outside the bearing.
  • An outer ring spacer 7 is provided adjacent to the outer ring 2, and the inner peripheral surface of the outer ring spacer 7 is opposed to the outer peripheral surface of the inner ring extension 6.
  • the oil supply / discharge oil mechanism KU includes an inner ring circumferential groove 8, an oil supply passage 9, a radial clearance ⁇ 1, an oil discharge port 10, a recessed portion 11, and a slope 1b.
  • the inner ring circumferential groove 8 is provided on the outer circumferential surface of the inner ring extension 6.
  • an oil supply passage 9 having an oil supply port 9 a for discharging the lubricant toward the inner ring circumferential groove 8 is formed in a part of the outer ring spacer 7 in the circumferential direction.
  • the oil supply passage 9 is formed in a stepped through hole shape that penetrates the recess 11 in the radial direction from the outer peripheral surface of the outer ring spacer 7. That is, the oil supply path 9 includes the oil supply port 9a formed of a communication hole communicating with a part of the recess 11 formed of a circumferential groove in the circumferential direction, and the counterbore portion 9b connected to the oil supply port 9a and opened to the outer peripheral surface. It consists of.
  • the counterbore portion 9b is concentric with the oil supply port 9a and has a larger diameter than the oil supply port 9a.
  • the lubricating oil supplied from the oil supply passage 9 is discharged from the oil supply port 9a, hits the inner ring circumferential groove 8, receives a centrifugal force from the inner ring 1 which is the raceway on the rotation side, and receives the outer ring spacer. Go to 7 indentations 11.
  • this lubricating oil proceeds in the same direction as the rotational direction L1 of the inner ring 1 through the recess 11 formed of a circumferential groove, and is discharged from the oil discharge port 10 and a notch 13 described later. Is done.
  • an oil discharge port 10 for discharging the lubricating oil to the outside is formed at a circumferential position different from the oil supply passage 9.
  • the oil discharge port 10 is formed so as to penetrate from the outer peripheral surface of the outer ring spacer 7 in the radial direction and communicate with the inner ring circumferential groove 8.
  • the radial clearance ⁇ ⁇ b> 1 is between the outer peripheral surface formed on the bearing side of the inner ring circumferential groove 8 in the outer peripheral surface of the inner ring extension 6 and the inner peripheral surface of the outer ring spacer 7. Is provided.
  • the lubricating oil introduced into the bearing from the radial clearance ⁇ 1 is guided to the inner ring raceway surface 1a via the slope 1b and the like.
  • the recess 11 is formed by a circumferential groove provided on the inner peripheral surface of the outer ring spacer 7.
  • the recessed portion 11 is opposed to the inner ring circumferential groove 8 and collects lubricating oil supplied from the oil supply passage 9 and bounced back in the inner ring circumferential groove 8.
  • the axial position P1 of the opening peripheral edge 12 connected to the aforementioned radial clearance ⁇ 1 and the axial position P2 of the opening peripheral edge 14 connected to the radial clearance ⁇ 1 of the inner ring circumferential groove 8 are defined.
  • the width dimension H1 of the recess 11 and the width dimension H2 of the inner ring circumferential groove 8 are the same.
  • the outer ring 2 which is a fixed-side raceway, is provided with a notch 13 for discharging the lubricating oil used for lubrication in the bearing to the outside of the bearing.
  • FIG. 4B is a front view (end view taken along line VIb-VIb) of the main part of FIG.
  • a notch 13 is provided on the outer ring end surface of the outer ring 2 on the side opposite to the axial direction from the side where the outer ring spacer 7 is provided.
  • the notch 13 is disposed between the oil supply passage 9 and the oil discharge port 10 along the rotation direction L ⁇ b> 1 of the inner ring 1.
  • the notch 13 is disposed with a phase angle of 90 degrees with respect to the oil supply passage 9 and with a phase angle of 180 degrees with respect to the oil discharge port 10, for example.
  • the inner ring extension 6 and the outer ring spacer 7 are provided with a labyrinth mechanism 15 that suppresses leakage of lubricating oil into adjacent bearings, for example.
  • the labyrinth mechanism 15 communicates with the oil supply passage 9 and the oil discharge port 10 (FIG. 1), and the wide portion and the narrow portion are continuous in the axial direction.
  • the wide portion includes a circumferential groove 16 provided on the outer circumferential surface of the other shoulder portion of the inner ring extension portion 6 and an inner circumferential surface of the outer ring spacer 7 facing the circumferential groove 16.
  • a plurality (two in this example) of the circumferential grooves 16 are arranged at intervals in the axial direction.
  • Each circumferential groove 16 has a cross-sectional shape that becomes smaller in diameter toward the end face side (upper side in FIG. 2) of the inner ring extension 6, in other words, is inclined so that the groove becomes deeper.
  • the narrow portion includes a protruding tip portion 17 of the outer peripheral surface of the inner ring extension portion 6 and an inner peripheral surface of the outer ring spacer 7 facing the protruding tip portion 17.
  • each circumferential groove 16 is formed in an inclined cross-sectional shape as described above, the lubricating oil supplied from the oil supply passage 9 and entering the labyrinth mechanism 15 is inclined by the centrifugal force due to the inner ring rotation. Move along the surface in the opposite direction to the leak side. Such a labyrinth mechanism 15 can prevent the lubricating oil from leaking into the adjacent bearing.
  • the number of circumferential grooves 16 may be three or more, or one.
  • a circumferential groove may be provided in the other shoulder portion of the outer ring spacer 7 having a concave cross section. Further, circumferential grooves may be provided in the inner ring extension 6 and the outer ring spacer 7 respectively.
  • the arrows in FIG. 1 indicate the flow of the lubricating oil.
  • the lubricating oil flows along the inner ring circumferential groove 8 on the outer peripheral surface of the inner ring extension 6. This cools the bearing.
  • the oil that has cooled the bearing is discharged from the oil discharge port 10 of the outer ring spacer 7.
  • the lubricating oil supplied from the oil supply passage 9 and bounced off at the inner ring circumferential groove 8 is collected in the recess 11 on the inner peripheral surface of the outer ring spacer 7 to suppress the intrusion of the lubricating oil into the bearing.
  • Lubricating oil collected in the recess 11 formed of a circumferential groove flows along the inner ring circumferential groove 8 and is smoothly discharged toward the oil discharge port 10.
  • an appropriate amount of lubricating oil for lubricating the bearing is supplied into the bearing through the radial clearance ⁇ 1, and then discharged out of the bearing.
  • the lubricating oil existing in the inner ring circumferential groove 8 receives a centrifugal force from the rotating inner ring 1 and advances toward the outer ring spacer 7.
  • the lubricating oil passes through the upper part of the radial clearance ⁇ 1.
  • the lubricating oil that has passed through the upper portion of the radial clearance ⁇ 1 is directed to the oil outlet 10 (FIG. 1).
  • the width dimensions H1, H2 FIG.
  • the lubricating oil existing in the inner ring circumferential groove 8 is transferred to the recess 11 by the centrifugal force from the inner ring 1. It can collect reliably and can prevent lubricating oil overflowing from the dent part 11 undesirably. Therefore, it is possible to prevent the lubricating oil from being undesirably discharged from locations other than the oil discharge port 10.
  • the recessed portion 11 of the outer ring spacer 7 may be narrower (that is, the dimension in the axial direction) toward the bottom surface.
  • the lubricating oil flows in the following (1) to (3) during the bearing operation.
  • the lubricating oil hits the inner ring circumferential groove 8 and is bounced back under the centrifugal force accompanying the inner ring rotation.
  • the rebounded lubricating oil travels toward the oil discharge port 10 along a narrow groove of the recess 11, in other words, a wedge-shaped groove.
  • the lubricating oil is discharged from the oil discharge port 10.
  • the lubricating oil is directed to the oil discharge port 10 along the narrow groove of the dent 11, the lubricating oil bounced off against the inner ring circumferential groove 8 can be efficiently collected in the dent 11. .
  • the recess 11 of the outer ring spacer 7 is connected to the circumferential groove 11a provided on the inner circumferential surface of the outer ring spacer 7 and the lower part of the circumferential groove 11a. It may have a circumferential groove 11b having a width dimension H1a larger than the circumferential groove 11a. In this case, the lubricating oil bounced off by hitting the inner ring circumferential groove 8 can be collected in the circumferential groove 11b having a large width dimension and drained smoothly.
  • FIG. 7 is a plan view showing the flow of lubricating oil in the rolling bearing device according to the fourth embodiment.
  • the oil drain port 10 of the outer ring spacer 7 may be provided so as to be connected in the tangential direction L2.
  • the lubricating oil supplied from the oil supply passage 9 of the outer ring spacer 7 hits an inner ring circumferential groove (not shown), bounces back, flows along the recess 11 of the outer ring spacer 7, and is discharged from the oil outlet 10. It is discharged smoothly without staying.
  • the recess 11 of the outer ring spacer 7 may be provided in an arc shape extending from the oil supply passage 9 of the outer ring spacer 7 to the oil discharge port 10.
  • the lubricating oil flowing through the recess 11 of the outer ring spacer 7 is blocked by the oil discharge port 10.
  • the blocked lubricating oil is quickly discharged from the oil discharge port 10.
  • FIG. 9 shows a sixth embodiment.
  • the inner ring circumferential groove 8 may have oil repellency.
  • the inner ring circumferential groove 8 By providing the inner ring circumferential groove 8 with, for example, a coating layer made of fluororesin or the like, the inner ring circumferential groove 8 having oil repellency can be obtained.
  • the lubricating oil existing in the inner ring circumferential groove 8 can be easily directed to the recessed portion 11 of the outer ring spacer 7 so that smooth drainage can be performed.
  • the outer peripheral surface portion of the inner ring extension 6 and the inner peripheral surface portion of the outer ring spacer 7 which are the portions forming the radial clearance ⁇ 1 also have oil repellency as described above. It is good as a thing. In this case, intrusion of the lubricating oil into the bearing can be suppressed.
  • FIG. 10 is a longitudinal sectional view schematically showing an example in which any of the above-described rolling bearing devices is used to support a vertical machine tool spindle.
  • two rolling bearing devices 28 and 28 including angular ball bearings are installed in the housing 29 in a combination of the back surfaces, and the main shaft 30 is rotatably supported by these rolling bearing devices 28 and 28.
  • the inner ring 1 in each bearing device 28 is positioned in the axial direction by inner ring positioning spacers 31, 31 and step portions 30 a, 30 a of the main shaft 30, and is fastened and fixed to the main shaft 30 by an inner ring fixing nut 32.
  • outer ring spacer 7 on the upper side of the main shaft and the outer ring 2 on the lower side of the main shaft are positioned and fixed in the housing 29 by outer ring holding lids 34 and 34.
  • An outer ring spacer 35 is interposed between the outer ring end surface on the upper side of the main shaft and the spacer width surface on the lower side of the main shaft.
  • the housing 29 is obtained by fitting a housing inner cylinder 29a and a housing outer cylinder 29b, and an oil passage groove 29c for cooling is provided in the fitting portion.
  • Supply oil passages 36 and 36 for supplying lubricating oil to the bearing devices 28 are formed in the housing inner cylinder 29a. These supply oil passages 36 are connected to a lubricating oil supply source (not shown).
  • the housing inner cylinder 29 a is formed with an oil drain groove 37 and an oil drain passage 38 for discharging the lubricating oil used for lubrication.
  • the oil drain groove 37 communicates with the notch 13 and the oil drain port 10 in each bearing device 28.
  • Each oil drain groove 37 is connected to an oil drain passage 38 extending in the main shaft axis direction, and the lubricating oil is discharged from the oil drain passage 38.
  • the rolling bearing devices 28 and 28 are used for supporting the machine tool main shaft 30 in this way, the lubricating oil bounced off by the inner ring circumferential groove 8 is collected in the recess 11 provided on the inner circumferential surface of the outer ring spacer 7. Since it can be discharged smoothly, a large amount of lubricating oil can be prevented from entering the bearing. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing. It is also possible to use the rolling bearing device according to the present embodiment for supporting a horizontal machine tool spindle.
  • the rolling bearing lubrication device is used, for example, for supporting a main shaft of a vertical machine tool.
  • the present invention is not limited to the vertical machine tool spindle, and may be used for supporting a horizontal machine tool spindle.
  • the rolling bearing lubrication device includes a plurality of (two in this example) rolling bearings BR arranged in the axial direction, and a supply / discharge oil mechanism KU provided to each rolling bearing BR. .
  • FIGS. 11 to 18 showing this embodiment the same or corresponding components as those in the first embodiment may be denoted by the same reference numerals and detailed description thereof may be omitted.
  • the oil supply / discharge mechanism KU is disposed above the bearing space S1 in each rolling bearing BR. Adjacent to the axial end of the outer ring 2, another spacer 7 ⁇ / b> A that is a separate body from the outer ring 2 is provided, and the inner peripheral surface of the other spacer 7 ⁇ / b> A is opposed to the outer peripheral surface of the inner ring extension 6. Yes. An oil supply / discharge oil mechanism KU is provided over the inner ring extension 6 and the other spacer 7A.
  • an oil supply passage 9 having an oil supply port 9a for discharging the lubricant toward the inner ring circumferential groove 8 is formed in a part of the other spacer 7A in the circumferential direction.
  • the oil supply passage 9 is formed in a stepped through hole shape that penetrates in the radial direction from the outer peripheral surface of the other spacer 7A.
  • a partition wall 6 a that partitions the bearing space and the inner ring circumferential groove 8 is provided in the inner ring extension 6.
  • Lubricating oil supplied from the reed oil supply passage 9 is (2) discharged from the refueling port 9a and hits the inner ring circumferential groove 8, and (3) receives centrifugal force from the inner ring 1 which is the raceway on the revolving side It hits the inner peripheral surface of the spacer 7A.
  • This lubricating oil is supplied to the bearing space S1 in the rolling bearing from the radial clearance ⁇ 1 between the outer peripheral surface of the inner ring extension 6 and the inner peripheral surface of the other spacer 7A.
  • the lubricating oil introduced into the bearing from the radial clearance ⁇ 1 is guided to the inner ring raceway surface 1a via the slope 1b and the like.
  • an oil groove 25 made of an annular groove is provided in the radial intermediate portion of the end face of the other spacer 7 ⁇ / b> A.
  • the adjacent rolling element 7A has an end face adjacent to the end face of the inner and outer rings 1 and 2 on the opposite side of the inner ring extension 6 to the end face of the spacer 7A.
  • An oil groove 25 is provided in communication with the bearing space S1 in the bearing BR to discharge the lubricating oil in the bearing.
  • the oil groove 25 is provided not only on the other spacer 7A in the lower rolling bearing BR in FIG. 11 but also on the end face of the other spacer 7A in the upper rolling bearing BR in FIG. As shown in FIG.
  • the oil groove 25 includes an outer ring inner peripheral surface 2 b, a rolling element outer peripheral surface 3 a, and a holding member that are opposite to the inner ring extension 6 in the rolling bearing BR
  • the cross-sectional area is larger than the cross-sectional area of the region S formed by the virtual cylindrical surface 4a including the outer peripheral surface of the vessel and the end surface 7a of the other spacer 7A.
  • the other spacer 7A is provided with a discharge port 26 that communicates with the oil groove 25 and discharges the lubricating oil in the oil groove 25 to the outside of the bearing.
  • the discharge port 26 is formed by cutting out a part of the circumference of the end face of the other spacer 7A from a part of the oil groove 25 in a rectangular shape in plan view outward in the radial direction.
  • 11 is a cross-sectional view taken along the line XI-XI in FIG. 16
  • FIG. 18 is a cross-sectional view taken along the line XVIII-XVIII in FIG.
  • the discharge port 26 has a depth dimension Db larger than the depth dimension Da of the oil groove 25, and the bottom surface 26 a of the discharge port 26 is connected to the bottom surface 25 a of the oil groove 25 via a stepped portion. It is connected.
  • a wall portion 14 that restricts the flow of the lubricating oil along the oil groove 25 is provided at the intersection of the other spacer 7 ⁇ / b> A where the oil groove 25 and the discharge port 26 communicate with each other. Yes. That is, in one of the other spacers 7A on the circumference where the discharge port 26 is provided, the wall portion 14 has a distance radius from the one circumferential surface portion 25b forming the oil groove 25 to the stepped portion or the vicinity of the stepped portion. It is provided so as to protrude outward in the direction.
  • the cross-sectional area of the wall portion 14 as seen by cutting along the cross-section including the bearing axis is substantially equal to the cross-sectional area of the oil groove 25.
  • FIG. 18 the cross-sectional area which looked at the cross
  • the said wall part 14 is arrange
  • a notch 2d penetrating outward in the radial direction of the bearing is provided in a part of the end surface of the outer ring 2 adjacent to the other spacer 7A in the circumferential direction.
  • This notch 2d has a counter bore 2c on the opposite side of the acting line L1 that forms a contact angle with the raceway surface 2a in a part of the outer ring 2 in the circumferential direction, near the raceway surface where the rolling element 3 is located (at least A notch is formed deeply to the extent that the raceway surface 2a does not interfere with the contact ellipse with the rolling element 3.
  • the inner ring extension 6 and the other spacer 7 ⁇ / b> A are provided with a labyrinth mechanism 15 that suppresses leakage of lubricating oil into adjacent bearings, for example.
  • the labyrinth mechanism 15 communicates with the oil supply passage 9 and the oil discharge port 10 (FIG. 13), and the wide portion and the narrow portion are continuous in the axial direction.
  • the wide portion includes a circumferential groove 16 provided on the outer peripheral surface of the other shoulder portion of the inner ring extension portion 6 and an inner peripheral surface of another spacer 7 ⁇ / b> A facing the circumferential groove 16. .
  • a plurality (two in this example) of the circumferential grooves 16 are arranged at intervals in the axial direction.
  • Each circumferential groove 16 is formed in a cross-sectional shape that becomes smaller in diameter toward the end face side (upper side in FIG. 17) of the inner ring extension 6, in other words, is inclined so that the groove becomes deeper.
  • the narrow portion includes a protruding tip portion 17 of the outer peripheral surface of the inner ring extension portion 6 and an inner peripheral surface of another spacer 7A facing the protruding tip portion 17.
  • each circumferential groove 16 is formed in an inclined cross-sectional shape as described above, the lubricating oil supplied from the oil supply passage 9 and entering the labyrinth mechanism 15 is inclined by the centrifugal force due to the inner ring rotation. Move along the surface in the opposite direction to the leak side. Such a labyrinth mechanism 15 can prevent the lubricating oil from leaking into the adjacent bearing.
  • the number of circumferential grooves 16 may be three or more, or one.
  • a circumferential groove may be provided in the other shoulder portion having a concave cross section in the other spacer 7A.
  • the oil groove 25 is an imaginary structure including an outer ring inner circumferential surface 2b, a rolling element outer circumferential surface, and a cage outer circumferential surface on the opposite side to the inner ring extension 6 in the cross section including the shaft center and the rolling element center in the rolling bearing BR. Since the cross-sectional area is larger than the cross-sectional area formed by the cylindrical surface 4a and the end surface 7a of the other spacer 7A, a certain amount of lubricating oil accumulates in the oil groove 25 and the lubricating oil stays inside the bearing. Can be prevented. Since the discharge port 26 has a depth dimension Db larger than the depth dimension Da of the oil groove 25, the lubricating oil flowing through the oil groove 25 easily flows to the discharge port 26 due to the action of gravity. Therefore, the lubricating oil can be smoothly discharged out of the bearing.
  • the rolling element 3 and the cage 4 can discharge the lubricating oil during high-speed rotation of the bearing, the circumferential direction of the end surface of the outer ring 2 adjacent to the other spacer 7A among the rolling bearings BR can be reduced. Since a notch 2d penetrating in the bearing radial direction is provided in part, part of the lubricating oil can be discharged out of the bearing through the notch 2d. For this reason, at the time of high-speed rotation of a bearing, it can suppress that lubricating oil retains in the one side part of rolling element 3 adjacent to other spacer 7A in bearing space S1. As a result, an increase in the stirring resistance inside the bearing can be prevented, a temperature rise inside the bearing can be suppressed, and high speed operation can be achieved.
  • the wall portion 14 that restricts the flow of the lubricating oil along the oil groove 25 is provided at the intersection where the oil groove 25 and the discharge port 26 communicate with each other, so that the lubricating oil that flows in the rotation direction of the bearing
  • the flow can be regulated by the wall portion 14, and the lubricating oil can be smoothly guided to the discharge port 26. Since this wall portion 14 is disposed at the center portion of the circumferential length L2 of the discharge port 26 of the other spacer 7A, the bearing 14 is disposed along the oil groove 25 even when the bearing rotates backward as indicated by the dotted line arrow in FIG. Thus, the lubricating oil flowing in the reverse rotation direction can be regulated by the wall portion 14 and smoothly guided to the discharge port 26.
  • Two or more outlets 26 may be provided in the other spacer 7A.
  • Each discharge port 26 communicates with the oil groove 25 to discharge the lubricating oil in the oil groove to the outside of the bearing.
  • the lubricating oil can be discharged more smoothly from the two or more discharge ports 26.
  • Notches 2d may be provided at a plurality of locations in the circumferential direction on the end face of the outer ring 2 adjacent to the other spacer 7A. In this case, a part of the lubricating oil can be discharged out of the bearing more smoothly through the two or more notches 2d.
  • Angular ball bearings may be any combination of a rear combination, a front combination, or a parallel combination. Further, the angular ball bearings may be combined in three or more rows.
  • FIG. 19 is a cross-sectional view schematically showing an example in which the rolling bearing lubrication device according to the seventh embodiment is used to support the spindle of a machine tool.
  • four rows of angular contact ball bearings combined in parallel with each other and four rows of so-called DTBT combination angular contact ball bearings are arranged in the axial direction and installed in the housing Hs. Support for rotation.
  • This combined angular contact ball bearing is configured to increase radial rigidity and axial rigidity and to enable high-speed operation, compared to a configuration in which two or three rows of angular ball bearings are combined.
  • These inner and outer rings 1 and 2 are fixed to the main shaft Sh and the housing Hs by an inner ring presser 19 and an outer ring presser 20, respectively.
  • an oil supply path 21 for supplying lubricating oil to the supply / exhaust oil mechanism KU, a cooling oil path 22 for discharging cooling oil that is the lubricating oil that has cooled the bearing, and a lubricating oil used for lubrication in the bearing
  • an oil discharge path (not shown) for discharging the oil.
  • the oil supply path 21 is connected to each oil supply path 9 and connected to a fuel supply pump 23 installed outside the housing Hs by piping. Using this oil pump 23, the lubricating oil can be forcibly pumped from the oil supply source to each oil supply path 9 via the oil supply path 21.
  • the cooling oil path 22 is connected to each oil outlet 10 and connected to a drain oil pump 24 installed outside the housing Hs. The lubricating oil that has cooled the bearing can be discharged out of the housing Hs through the oil discharge path 22 using the oil discharge pump 24.
  • the oil discharge path 22 is connected to each discharge port 26 and each notch 2d shown in FIG. 18, and discharges the lubricating oil used for lubrication in the bearing to the outside of the housing Hs by gravity and centrifugal force due to rotation of the inner ring.
  • the lubricating oil provided for lubrication in the bearing can be discharged by gravity and centrifugal force without using a pump or the like, excessive lubricating oil does not flow into the bearing.
  • the oil grooves 25 are provided on the end surfaces of the other spacers 7A. It is possible to prevent the lubricating oil from staying in the vicinity of the boundary with the adjacent bearing in the bearing space S1 in the bearing. Further, since a notch 2d penetrating in the bearing radial direction is provided in a part of the end surface of the outer ring 2 adjacent to the other spacer 7A in the circumferential direction, a part of the lubricating oil is bearing through the notch 2d. Can be discharged outside.
  • FIG. 20 shows an eighth embodiment of the present invention.
  • both the recess 11 and the oil groove 25 are provided. Therefore, the effects of the recess 11 and the oil groove 25 described above can be combined.
  • a rolling bearing device includes a rolling bearing in which a plurality of rolling elements held by a cage are interposed between raceway surfaces of inner and outer rings, and lubricating oil serving as a bearing cooling medium in the bearing.
  • a rolling bearing device having a supply / discharge oil mechanism for supplying and discharging outside the bearing, between the inner rings adjacent to one end face of the inner ring and having an outer diameter within a radial width of one end face of the outer ring A seat is provided, an outer ring spacer is provided adjacent to one end surface of the outer ring and an inner peripheral surface thereof is opposed to the outer peripheral surface of the inner ring spacer, and the oil supply / drainage mechanism is provided on the outer peripheral surface of the inner ring spacer.
  • the first throttle that restricts the amount of lubricating oil that is provided in the clearance of the guide and is guided from the circumferential groove to one end surface of the outer ring
  • An annular oil retaining groove that is provided on one end surface of the outer ring and communicates with the first throttle portion and receives lubricating oil guided from the first throttle portion, one end surface of the outer ring, and the outer ring
  • a second throttle part provided between one end face of the inner ring spacer facing one end face, communicating with the oil retaining groove and the bearing space of the inner and outer rings, respectively, and restricting the amount of lubricating oil entering the bearing space;
  • the lubricating oil flows along the circumferential groove on the outer peripheral surface of the inner ring spacer. This cools the bearing.
  • the oil that has cooled the bearing is divided into, for example, one that is discharged and one that passes through the first throttle portion and flows into the oil retaining groove for bearing lubrication. At least a part of the lubricating oil flowing in the oil retaining groove passes through the second throttle portion and enters the bearing space.
  • the oil supply / discharge oil mechanism may be provided on the outer peripheral surface of the outer ring, and may include an oil discharge port that communicates with the oil retaining groove and discharges the lubricating oil.
  • Lubricating oil that has flowed into the oil retaining groove after passing through the first throttle part is collected through the oil outlet of the outer ring, and that that passes through the second throttle part and enters the bearing space. Divided.
  • the oil drain port is provided on the outer peripheral surface of the outer ring in this way, the oil drain efficiency can be increased as compared with a configuration in which the oil drain port is not provided on the outer peripheral surface of the outer ring. Two or more oil outlets of the outer ring may be provided. In this case, the oil drainage efficiency can be further improved.
  • the circumferential groove of the inner ring spacer may have a concave cross section when the inner ring spacer is cut along a plane including the bearing axis.
  • the lubricating oil supplied from the oil supply passage is bounced back to the groove bottom surface of the circumferential groove having a concave cross section, and is directed to the first throttle portion or the like by the centrifugal force accompanying the rotation of the inner ring.
  • the oil supply / discharge mechanism includes an oil discharge port provided in the outer ring spacer, and the oil discharge port communicates with a circumferential groove at a circumferential position different from the oil supply port, and discharges lubricating oil. It may be.
  • the lubricating oil that flows along the circumferential groove of the inner ring spacer is divided into one that is discharged from the oil outlet of the outer ring spacer and one that passes through the first throttle part for bearing lubrication. You may provide the barrier which regulates the flow along the circumferential groove
  • the lubricating oil flowing along the circumferential groove with the rotation of the inner ring hits the barrier and is easily collected at the oil discharge port. Thereby, it can suppress that lubricating oil retains inside a bearing, Therefore, increase of the stirring resistance inside a bearing can be prevented.
  • the barrier may be disposed at the center of the circumferential length at the oil outlet of the outer ring spacer.
  • the lubricating oil flowing in the forward rotation direction along the circumferential groove can be regulated by the barrier and smoothly guided to the oil discharge port.
  • the lubricating oil flowing in the reverse rotation direction along the circumferential groove can be regulated by the barrier and smoothly guided to the oil discharge port.
  • the barrier may include an extending portion extending to the vicinity of the bottom surface of the circumferential groove in the inner ring spacer.
  • the lubricating oil flowing along the circumferential groove of the inner ring spacer can be reliably collided by the barrier.
  • recovered from an oil discharge port can be improved compared with the barrier without an extension part.
  • the valve may be a valve structure that can move according to the flow direction of the lubricating oil.
  • the lubricating oil can be smoothly guided to the oil discharge port by moving the barrier according to the flow direction of the lubricating oil regardless of whether the bearing is rotating forward or reverse.
  • the barrier is inclined so as to reach the central portion of the circumferential length of the oil discharge port from one side in the circumferential direction of the oil discharge port toward the opening edge radially outward.
  • An inclined part may be included. In this case, since the lubricating oil flows smoothly along the inclined portion, it is possible to improve the recovery efficiency of the lubricating oil recovered from the oil discharge port.
  • the barrier has two wall portions arranged in the axial direction at the oil discharge port, and each wall portion extends radially from one side in the radial direction at the oil discharge port to the radial direction at the oil discharge port.
  • the two wall portions arranged in the axial direction may be provided so as to incline so as to reach the outer circumferential other side portion and to cross each other in the axial direction. In this case, the lubricating oil smoothly flows along either one of the wall portions regardless of whether the bearing is rotating forward or backward, so that the recovery efficiency of the lubricating oil recovered from the oil discharge port can be improved.
  • the amount of lubricating oil entering the bearing space may be controlled by managing the clearance between the first and second throttle portions.
  • Any of the above-mentioned rolling bearing devices may be used for supporting the machine tool spindle.
  • an inner ring outer diameter surface 1b, an inclined surface 1c following the inner ring outer diameter surface 1b, and an inclined counter bore 1d are formed on both axial sides of the raceway surface 1a of the inner ring 1, respectively.
  • the inner ring outer diameter surface 1b in this example extends in the width direction from the biased side of the action line L that forms a contact angle with the raceway surface 1a.
  • the inclined surface 1c following the outer peripheral edge portion of the inner ring outer diameter surface 1b in the axial direction is formed in a cross-sectional shape that is inclined so as to reach the inner diameter side toward one side in the axial direction (upward in FIG. 22).
  • Outer ring inner diameter surfaces 2b and 2b are respectively formed on both axial sides of the raceway surface 2a of the outer ring 2, and the cage 4 is configured to be guided by these outer ring inner diameter surfaces 2b and 2b.
  • an inner ring spacer 6 is provided adjacent to one end face of the inner ring 1, and the outer diameter 6 a of the inner ring spacer 6 is located within the radial width of one end face of the outer ring 2. is doing.
  • an outer ring spacer 7 is provided adjacent to one end surface of the outer ring 2, and the inner peripheral surface of the outer ring spacer 7 is opposed to the outer peripheral surface of the inner ring spacer 6.
  • the oil supply / drainage mechanism KU includes a circumferential groove 8 provided on the outer peripheral surface of the inner ring spacer 6, an oil supply passage 9 provided in the outer ring spacer 7, and an oil discharge port 10 provided in the outer ring spacer 7.
  • the first throttle part 40, the annular oil retaining groove 42, the oil outlet 43 of the outer ring 2, and the second throttle part 41 are provided.
  • a circumferential groove 8 On the outer peripheral surface of the inner ring spacer 6, there is provided a circumferential groove 8 having a concave cross section when the inner ring spacer 6 is cut along a plane including the bearing axis.
  • an oil supply passage 9 having an oil supply port 9 a that discharges lubricating oil toward the circumferential groove 8 is formed in a part of the outer ring spacer 7 in the circumferential direction.
  • the oil supply passage 9 is formed in a stepped through hole shape that penetrates in the radial direction from the outer peripheral surface of the outer ring spacer 7. As shown in FIG. 25, the lubricating oil supplied from the oil supply passage 9 is discharged from the oil supply port 9 a and supplied to the circumferential groove 8.
  • the lubricating oil proceeds along the circumferential groove 8 in the same direction as the rotation direction L1 of the inner ring 1 (FIG. 21), and is used for cooling the bearing.
  • the lubricating oil used for cooling is discharged from the oil discharge ports 10 and 43 (FIG. 21) and a notch 15 described later.
  • an oil discharge port 10 for discharging the lubricating oil to the outside is formed at a circumferential position different from the oil supply passage 9.
  • the oil discharge port 10 is formed so as to penetrate from the outer peripheral surface of the outer ring spacer 7 in the radial direction and communicate with the circumferential groove 8.
  • an adjacent bearing is provided between the outer peripheral surface of the inner ring spacer 6 that is opposite to the bearing in the axial direction and the inner peripheral surface of the outer ring spacer 7 that faces the outer peripheral surface.
  • a labyrinth mechanism RK that suppresses leakage of lubricating oil is provided.
  • the labyrinth mechanism RK communicates with the oil supply passage 9 and the oil discharge port 10 (FIG. 21), and the wide portion and the narrow portion are continuous in the axial direction.
  • the wide portion includes a circumferential groove 6b provided on the outer circumferential surface of the inner ring spacer 6 on the opposite side in the axial direction, and an inner circumferential surface of the outer ring spacer 7 facing the circumferential groove 6b.
  • a plurality of the circumferential grooves 6b are arranged at intervals in the axial direction.
  • the narrow portion includes a protruding tip portion of the outer peripheral surface of the inner ring spacer 6 and an inner peripheral surface of the outer ring spacer 7 facing the protruding tip portion.
  • the lubricating oil moves in the direction opposite to the leakage side along the circumferential groove 6b due to the centrifugal force generated by the inner ring rotation. It is possible to suppress the leakage of the lubricating oil.
  • a circumferential groove may be provided on the inner peripheral surface of the outer ring spacer 7. Further, circumferential grooves may be provided in the inner ring spacer 6 and the outer ring spacer 7 respectively.
  • FIG. 23 is an enlarged view of the main part of FIG.
  • the inner ring spacer 6 has a circumferential groove 8 in the clearance between the outer circumferential surface opposite to the labyrinth mechanism RK in the axial direction and the inner circumferential surface of the outer ring spacer 7.
  • a first throttle portion 40 is provided for reducing the amount of lubricating oil guided to one end surface of the outer ring 2. Accordingly, the oil that flows along the circumferential groove 8 of the inner ring spacer 6 and cools the bearing is divided into one that is discharged from the oil discharge port 10 and one that passes through the first throttle 40 for bearing lubrication. .
  • an upper limit value and a lower limit value of the axial clearance ⁇ 1 forming the first throttle portion 40 are managed, and thereby the amount of lubricating oil guided to the bearing side can be controlled.
  • an annular oil retaining groove 42 is provided on one end surface of the outer ring 2.
  • the oil retaining groove 42 is a circumferential groove that communicates with the first throttle portion 40 and accommodates lubricating oil guided from the first throttle portion 40.
  • the oil retaining groove 42 is formed within a radial width at one end surface of the outer ring 2 and has a rectangular cross section.
  • FIG. 22 is a front view of the outer ring 2.
  • an oil drain port 43 is provided on the outer peripheral surface of the outer ring 2.
  • the oil discharge ports 43 are provided at, for example, two or more circumferentially equidistant positions (when two oil discharge ports 43 and 43 are provided, the oil discharge ports 43 and 43 are at a diagonal position of 180 degrees). It has been.
  • the oil discharge ports 43 and 43 communicate with the oil retaining groove 42 and discharge the lubricating oil.
  • each oil discharge port 43 in this example is formed in a long hole shape having a circumferential length L3 longer than the axial length L2, and extends from the oil retaining groove 42 along the circumferential direction.
  • each oil outlet 43 and the oil retaining groove 42 of the outer ring 2 are on the opposite side of the outer ring 2 opposite to the biased side of the action line L that forms a contact angle with the raceway surface 2a. Is provided. It is possible to provide two or more oil drain ports 43 in the circumferential direction unevenly, and it is also possible to provide the oil drain ports 43 only in one circumferential direction.
  • a second throttle part 41 is provided between the one end surface of the outer ring 2 and one end surface of the inner ring spacer 6 facing the one end surface of the outer ring 2, a second throttle part 41 is provided.
  • the second throttle portion 41 communicates with the oil retaining groove 42 and the bearing space A1 of the inner and outer rings 1 and 2, respectively, and throttles the amount of lubricating oil that enters the bearing space A1. That is, only the lubricating oil that has passed through the first throttle portion 40 and the second throttle portion 41 sequentially from the circumferential groove 8 of the inner ring spacer 6 enters the bearing space A1.
  • the “large amount of lubricating oil” refers to an amount of lubricating oil that causes the bearing oil to have a stirring resistance, and the temperature of the bearing rises above a temperature determined by experiments, simulations, or the like.
  • the outer ring 2 is separated from the inner ring 2 by processing the entire width of the radial width surface on the inner diameter side with respect to the oil retaining groove 42 in one end surface of the outer ring 2.
  • a second throttle portion 41 that forms a radial clearance ⁇ ⁇ b> 2 is provided.
  • an upper limit value and a lower limit value of the radial clearance ⁇ ⁇ b> 2 forming the second throttle portion 41 are managed.
  • the second throttle part 41 is provided. May be provided.
  • the outer ring 2 which is a fixed-side raceway ring, is provided with a notch 15 for discharging the lubricating oil provided for lubrication in the bearing space A1 to the outside of the bearing.
  • a cutout portion 15 is provided on the other end surface of the outer ring 2 on the opposite side in the axial direction where the outer ring spacer 7 is provided.
  • the notch 15 is disposed between the oil supply passage 9 and the oil discharge port 10 along the rotation direction L ⁇ b> 1 of the inner ring 1.
  • the notch 15 is disposed with a phase angle of 90 degrees with respect to the oil supply passage 9 and with a phase angle of 180 degrees with respect to the oil discharge port 10, for example.
  • the lubricating oil flows along the circumferential groove 8 of the inner ring spacer 6. This cools the bearing.
  • the oil that has cooled the bearing is divided into oil that is discharged from the oil discharge port 10 of the outer ring spacer 7 and oil that passes through the first throttle portion 40 and flows into the oil retaining groove 42 for bearing lubrication. Further, the lubricating oil that has flowed into the oil retaining groove 42 is divided into one that is collected through the oil outlet 43 of the outer ring 2 and one that passes through the second throttle portion 41 and enters the bearing space A1.
  • the amount of lubricating oil that enters the bearing space A1 can be suppressed. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.
  • the oil drainage port 43 is provided on the outer peripheral surface of the outer ring 2, so that the oil drainage efficiency can be improved as compared with the configuration in which the oil drain port 43 is not provided on the outer peripheral surface of the outer ring 2.
  • the oil discharge efficiency can be further improved. Since the circumferential groove 8 of the inner ring spacer 6 is formed in a concave cross section, the lubricating oil supplied from the oil supply passage 9 rebounds to the groove bottom surface 8a of the circumferential groove 8 having a concave cross section to accompany the rotation of the inner ring. Centrifugal force is directed toward the oil outlet 10 of the outer ring spacer 7 and the first throttle 40.
  • An outer diameter 6a of the inner ring spacer 6 is provided thick in the radial direction so as to be positioned within a radial width of one end surface of the outer ring 2, and the circumferential groove 8 of the inner ring spacer 6 is formed radially outward. Since the outer ring 6a of the inner ring spacer 6 has an outer diameter 6a that is located within the radial width of one end surface of the inner ring 1, the groove bottom can be deepened and the lubricant can be supplied. The cross section can be enlarged. As a result, a sufficient amount of lubricant necessary for cooling and lubrication can be supplied to the circumferential groove 8, and in particular, the cooling effect can be further enhanced.
  • each oil outlet 43 and oil retaining groove 42 of the outer ring 2 are provided on the opposite side of the outer ring 2 opposite to the side of the acting line L that forms a contact angle with the raceway surface 2a, The load that 2 can tolerate is not reduced. For this reason, the rigidity of the outer ring 2 can be maintained high, and a reduction in bearing life can be prevented.
  • a barrier 27 that restricts the flow of the lubricating oil along the circumferential groove 8 may be provided in the oil outlet 10 of the outer ring spacer 7.
  • the barrier 27 is in the form of a rectangular plate extending in the radial direction and disposed at the center of the circumferential length La of the oil outlet 10 of the outer ring spacer 7.
  • the barrier 27 extends from the opening edge of the oil discharge port 10 to the vicinity of the radially inner periphery of the oil discharge port 10. According to this barrier 27, the lubricating oil flowing along the circumferential groove 8 with the rotation of the inner ring hits the barrier 27 and is easily collected at the oil discharge port 10.
  • the barrier 27 is disposed at the central portion of the circumferential length La in the oil discharge port 10 of the outer ring spacer 7, the lubricating oil is supplied along the circumferential groove 8 regardless of whether the bearing is rotating forward or reverse. It can be regulated by the barrier 27 and smoothly guided to the oil discharge port 10.
  • the barrier 27 may include an extending portion 27 a extending to the vicinity of the bottom surface of the circumferential groove 8 in the inner ring spacer 6.
  • the lubricating oil flowing along the circumferential groove 8 can be reliably collided by the barrier 27.
  • recovered from the oil discharge port 10 can be improved compared with the barrier without the extension part 27a.
  • the barrier 27A may be tapered.
  • the barrier 27A in this example has a triangular prism shape, for example, and includes inclined portions 27Aa and 27Aa that are inclined so as to reach the central portion P1 of the circumferential length La at the oil discharge port 10.
  • the inclination angles ⁇ 1 and ⁇ 1 of the inclined portions 27Aa and 27Aa with respect to the radial direction passing through the central portion P1 are set to the same angle and are defined as angles that do not impede the recovery of drained oil.
  • the distance Lb between the radially inner end of one inclined portion 27Aa and the radially inner end of the other inclined portion 27Aa is inserted into the barrier 27A from the outer diameter direction of the oil discharge port 10.
  • the circumferential length (width dimension) La of the oil discharge port 10 is substantially the same.
  • the inclined portions 27Aa and 27Aa are provided so that the side connecting these both end portions is parallel to a tangent line passing through the central portion P1 in the outer ring spacer 7.
  • each inclined portion 27Aa allows the lubricating oil flowing along the circumferential groove 8 to flow smoothly along the inclined portion 27Aa and be smoothly guided to the oil discharge port 10 regardless of whether the bearing rotates forward or backward. .
  • FIG. 29 is an example in which the barrier 27B is tapered like FIG. 28, but by forming the barrier 27B into a two-part structure, the end portion on the radially inner side of one inclined portion 27Ba The distance Lb from the radially inward end of the other inclined portion 27Ba is made larger than the circumferential length La of the oil discharge port 10. The end of each inclined portion 27Ba extends to the vicinity of the bottom surface of the circumferential groove 8 in the inner ring spacer 6. When the barrier 27B extends over the inner ring spacer 6 and the outer ring spacer 7 in this way, the barrier 27B is inserted from the outer diameter direction of the oil discharge port 10 in consideration of assembling properties.
  • each inclined part 27Ba can be inserted from the outer diameter direction of the oil discharge port 10 to assemble the barrier 27B easily, and the manufacturing cost can be reduced.
  • the barrier 27C may be a valve structure that can move according to the flow direction of the lubricating oil.
  • FIG. 30 (A) is a plan view of the main part showing the state when the inner ring rotates counterclockwise in the figure
  • FIG. 30 (B) shows the state when the inner ring rotates clockwise in the figure. It is a top view of the principal part showing.
  • One end in the longitudinal direction of the valve body 27Ca is swingably supported inward of the oil outlet 10 of the outer ring spacer 7 in the radial direction.
  • the lubricating oil flowing in the inner ring rotating direction along the circumferential groove 8 presses and moves the other end in the longitudinal direction of the valve body 27Ca.
  • the lubricating oil can be smoothly guided to the oil discharge port 10 by moving the barrier 27C in accordance with the flow direction of the lubricating oil regardless of the forward rotation and the reverse rotation of the bearing.
  • the structure can be simplified.
  • FIG. 32 is an enlarged perspective view showing the main part of the outer ring spacer 7 from the inner diameter side
  • FIG. 33 is a plan view of the main part of the outer ring spacer 7.
  • each of the walls 27 ⁇ / b> Da and 27 ⁇ / b> Da extends from the radially inner side of the oil outlet 10 toward the radially outer side of the oil outlet 10.
  • the two wall portions 27Da and 27Da that are inclined so as to reach the other side portion and are arranged in the axial direction are provided so as to intersect each other. In this case, the lubricating oil smoothly flows along either one of the wall portions 27Da regardless of whether the bearing is rotating forward or backward, thereby improving the recovery efficiency of the lubricating oil recovered from the oil discharge port 10. Can do.
  • the rolling bearing devices 28, 28 according to the application form can be applied in the same manner as the rolling bearing application example according to the embodiment of the present invention shown in FIG. 10, and the first and second restricting portions 40 are applied to each rolling bearing device 28. , 41 (FIG. 21), the amount of lubricating oil that enters the bearing space can be suppressed. For this reason, the temperature rise of the bearing due to the stirring resistance of the lubricating oil can be suppressed, and the bearing can be rotated at high speed.
  • a rolling bearing device includes a rolling bearing in which a plurality of rolling elements held by a cage are interposed between raceway surfaces of inner and outer rings, and lubricating oil serving as a bearing cooling medium in the bearing.
  • a rolling bearing device having a supply and discharge oil mechanism for supplying and discharging to the outside of the bearing, wherein the inner ring is provided with an inner ring extension portion extending in the axial direction, and an inner peripheral surface is adjacent to the outer ring and the inner ring surface is extended.
  • An outer ring spacer is provided opposite the inner ring, and the oil supply / discharge oil mechanism is provided in an inner ring circumferential groove provided on the outer circumferential surface of the inner ring extension, and in the outer ring spacer, and lubricating oil is supplied to the inner ring circumferential groove.
  • An oil supply passage having an oil supply port that discharges toward the outer ring, an oil discharge port that is provided in the outer ring spacer, communicates with an inner ring circumferential groove at a circumferential position different from the oil supply port, and discharges lubricating oil;
  • a spacer end surface adjacent to the outer ring in the outer ring spacer, and the bearing in the bearing It is provided on the surface adjacent to the bearing end facing the seat end surface, and passes through the clearance between the inner peripheral surface of the outer ring spacer and the outer peripheral surface of the inner ring, and enters the bearing space of the inner and outer rings.
  • a suppression valve that suppresses the amount of oil.
  • the lubricating oil when lubricating oil is supplied from the oil supply passage of the outer ring spacer during bearing operation, the lubricating oil flows along the inner ring circumferential groove on the outer peripheral surface of the inner ring extension. This cools the bearing. The oil that has cooled the bearing is discharged from the oil outlet of the outer ring spacer. The lubricating oil supplied to the inner ring circumferential groove receives a centrifugal force and collides with the inner circumferential surface of the outer ring spacer. A part of the collided lubricating oil tends to enter the bearing space from the gap between the inner peripheral surface of the outer ring spacer and the outer peripheral surface of the inner ring.
  • the suppression valve is provided on the surface adjacent to the spacer end surface of the outer ring spacer and the bearing end portion, the amount of lubricating oil entering the bearing space can be suppressed.
  • the control valve can prevent a large amount of lubricating oil from entering the bearing space. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.
  • a circumferential groove may be provided on the outer circumferential surface of the inner ring on the bearing side of the clearance, and the circumferential groove and the suppression valve may form a labyrinth structure.
  • the labyrinth structure can further suppress the intrusion of lubricating oil into the bearing space.
  • a radial lip extending inward in the radial direction and an axial lip extending in the axial direction are provided at the distal end portion of the suppression valve, respectively, and between the radial lip and the groove bottom surface of the circumferential groove.
  • a radial clearance may be provided, and an axial clearance may be provided between the axial lip and the groove side surface of the circumferential groove. In this case, the penetration of the lubricating oil into the bearing space can be further suppressed by the radial clearance and the axial clearance.
  • the suppression valve may be made of an elastic body or rubber.
  • the tip of the suppression valve may be provided with a lip that makes light contact with the inner ring. Since this lip is always exposed to the lubricating oil during the operation of the bearing, wear of the lip is suppressed. Since the lip is in light contact with the inner ring, the penetration of the lubricating oil into the bearing space from between the tip of the lip and the inner ring is prevented.
  • the suppression valve may be provided with a hole for supplying lubricating oil into the bearing space. Lubricating oil necessary for bearing lubrication is supplied into the bearing space from the hole. Two or more holes of the suppression valve may be provided. The holes may be arranged at equal intervals along the circumferential direction. In these cases, the bearing can be more reliably lubricated.
  • the oil outlet of the outer ring spacer may be provided with a barrier that restricts the flow of the lubricating oil along the circumferential groove of the inner ring.
  • the lubricating oil that flows along the inner ring circumferential groove with the rotation of the inner ring hits the barrier and is easily collected at the oil discharge port. Thereby, it can suppress that lubricating oil retains inside a bearing, Therefore, increase of the stirring resistance inside a bearing can be prevented.
  • the barrier may be disposed at the center of the circumferential length at the oil outlet of the outer ring spacer.
  • the lubricating oil flowing in the forward rotation direction along the inner ring circumferential groove can be regulated by the barrier and smoothly guided to the oil discharge port.
  • the lubricating oil flowing in the reverse rotation direction along the inner ring circumferential groove can be regulated by the barrier and smoothly guided to the oil discharge port.
  • the barrier may include an extending portion extending to the vicinity of the bottom surface of the inner ring circumferential groove in the inner ring extension.
  • the lubricating oil flowing along the inner ring circumferential groove can be reliably collided by the barrier.
  • recovered from an oil discharge port can be improved compared with the barrier without an extension part.
  • the valve may be a valve structure that can move according to the flow direction of the lubricating oil.
  • the lubricating oil can be smoothly guided to the oil discharge port by moving the barrier according to the flow direction of the lubricating oil regardless of whether the bearing is rotating forward or reverse.
  • the barrier is inclined so as to reach the central portion of the circumferential length of the oil discharge port from one side in the circumferential direction of the oil discharge port toward the opening edge radially outward.
  • An inclined part may be included. In this case, since the lubricating oil flows smoothly along the inclined portion, it is possible to improve the recovery efficiency of the lubricating oil recovered from the oil discharge port.
  • the barrier has two wall portions arranged in the axial direction at the oil discharge port, and each wall portion extends radially from one side in the radial direction at the oil discharge port to the radial direction at the oil discharge port.
  • the two wall portions arranged in the axial direction may be provided so as to incline so as to reach the outer circumferential other side portion and to cross each other in the axial direction. In this case, the lubricating oil smoothly flows along either one of the wall portions regardless of whether the bearing is rotating forward or backward, so that the recovery efficiency of the lubricating oil recovered from the oil discharge port can be improved.
  • Any of the above-mentioned rolling bearing devices may be used for supporting the machine tool spindle.
  • the inner ring extension 6 is provided with a partition wall B1 that partitions the bearing space A1 and the inner ring circumferential groove 8 and forms a circumferential groove 6a described later.
  • a radial clearance ⁇ 3 is provided between the outer peripheral surface of the outer peripheral surface of the inner ring extension 6 that is opposite to the outer peripheral surface of the partition wall B1 in the axial direction and the inner peripheral surface of the outer ring spacer 7 facing the outer peripheral surface, for example, A radial clearance ⁇ 3 is provided to prevent the lubricating oil from leaking to adjacent bearings or the like.
  • the oil supply / discharge oil mechanism KU shown in this specific example includes an inner ring circumferential groove 8, an oil supply passage 9, a radial clearance ⁇ 1, an oil discharge port 10, and a suppression valve as a suppression valve.
  • the inner ring circumferential groove 8 is provided on the outer peripheral surface of the inner ring extension 6.
  • an oil supply passage 9 having an oil supply port 9a for discharging lubricating oil toward the inner ring circumferential groove 8 is formed in a part of the outer ring spacer 7 in the circumferential direction.
  • the oil supply passage 9 is formed in a stepped through hole shape that penetrates in the radial direction from the outer peripheral surface of the outer ring spacer 7.
  • the lubricating oil supplied from the oil supply passage 9 is discharged from the oil supply port 9 a and supplied to the inner ring circumferential groove 8.
  • the lubricating oil travels along the inner ring circumferential groove 8 in the same direction as the rotation direction L1 of the inner ring 1 and is used for cooling the bearing.
  • the lubricating oil used for cooling is discharged from the oil discharge port 10 and a notch 13 described later.
  • an oil discharge port 10 for discharging the lubricating oil to the outside is formed at a circumferential position different from the oil supply passage 9.
  • the oil discharge port 10 is formed so as to penetrate from the outer peripheral surface of the outer ring spacer 7 in the radial direction and communicate with the inner ring circumferential groove 8.
  • the radial clearance ⁇ 1 is defined between the outer peripheral surface of the inner ring extension 6 and the outer peripheral surface formed on the bearing side of the inner ring circumferential groove 8 and the inner peripheral surface of the outer ring spacer 7. Between. In other words, a radial clearance ⁇ 1 is provided between the outer peripheral surface of the partition wall B1 in the inner ring extension 6 and the inner peripheral surface of the outer ring spacer 7.
  • the lubricating oil is introduced into the bearing space A1 of the inner and outer rings 1 and 2 through the clearance ⁇ 1 and the radial clearance ⁇ 2 between the suppression valve CS and the circumferential groove 6a.
  • the suppression valve CS suppresses the amount of lubricating oil that enters the bearing space A1.
  • the suppression valve CS is provided on a surface adjacent to the spacer end surface adjacent to the outer ring 2 in the outer ring spacer 7 and the bearing end portion facing the spacer end surface in the bearing.
  • an annular recess 7a having a step is formed in the inner peripheral portion of the spacer end surface, and the suppression valve CS is fitted and fixed to the annular recess 7a.
  • the suppression valve CS is made of an elastic body or rubber, and has a base end portion Sa having a substantially rectangular cross section and a lip Sb extending radially inward from the inner peripheral edge of the base end portion Sa.
  • the base end portion Sa and the lip Sb are integrally formed by a mold (not shown).
  • the base end portion Sa is fitted into the annular recess 7a of the outer ring spacer 7 to prevent the base end portion Sa and the lip Sb from entering the bearing space A1.
  • a circumferential groove 6a is provided on the bearing side of the clearance ⁇ 1, and the circumferential groove 6a and the suppression valve CS form a labyrinth structure.
  • the circumferential groove 6a is composed of a groove bottom surface 6aa and groove side surfaces 6ab and 6ac connected to both side edges in the axial direction of the groove bottom surface 6aa.
  • One groove side surface 6ab is connected to the gap ⁇ 1, and the other groove side surface 6ac is connected. It is connected to the outer peripheral surface of the inner ring main body 6.
  • One groove side surface 6ab is formed in a cross-sectional shape that is inclined so as to reach the inner ring main body portion side toward the radially inner side (groove bottom surface 6aa), and the other groove side surface 6ac is the inner ring toward the radially outer side.
  • the cross-sectional shape is inclined so as to reach the main body side.
  • a radial clearance ⁇ 2 is provided between the lip Sb and the groove bottom surface 6aa of the circumferential groove 6a. Therefore, only the lubricating oil that sequentially passes through the clearances ⁇ 1 and ⁇ 2 enters the bearing space A1 from the inner ring circumferential groove 8.
  • the suppression valve CS By providing not only the clearance ⁇ 1 but also the radial clearance ⁇ 2 by the suppression valve CS, the amount of lubricating oil entering the bearing space A1 can be suppressed.
  • the “large amount of lubricating oil” refers to an amount of lubricating oil that causes the bearing oil to have a stirring resistance, and the temperature of the bearing rises above a temperature determined by experiments, simulations, or the like.
  • the outer ring 2 which is a fixed-side raceway ring, is provided with a notch 13 for discharging the lubricating oil used for lubrication inside the bearing to the outside of the bearing.
  • a cutout portion 13 is provided on the outer ring end surface of the outer ring 2 on the opposite side in the axial direction from the side where the outer ring spacer 7 is provided.
  • the notch 13 is disposed between the oil supply passage 9 and the oil discharge port 10 along the rotation direction L ⁇ b> 1 of the inner ring 1.
  • the notch 13 is disposed with a phase angle of 90 degrees with respect to the oil supply passage 9 and with a phase angle of 180 degrees with respect to the oil discharge port 10, for example.
  • the suppression valve CS by providing not only the clearance ⁇ 1 but also the radial clearance ⁇ 2 by the suppression valve CS, the amount of lubricating oil entering the bearing space A1 can be suppressed.
  • the suppression valve CS By providing the suppression valve CS in this way, a large amount of lubricating oil can be prevented from entering the bearing space A1. Since a circumferential groove 6a is provided on the bearing side of the outer peripheral surface of the inner ring 1 with respect to the clearance ⁇ 1, and the circumferential groove 6a and the suppression valve CS form a labyrinth structure, the structure without the labyrinth structure Infiltration of the lubricating oil into the bearing space A1 can be further suppressed.
  • a configuration may be adopted in which a radial lip Sb extending inward in the radial direction and an axial lip Sc extending in the axial direction are provided at the distal end portion of the suppression valve CS. These lips Sb and Sc are formed in an L-shaped cross section.
  • a radial clearance ⁇ 2 is provided between the radial lip Sb and the groove bottom surface 6aa of the circumferential groove 6a, and an axial clearance ⁇ 4 is provided between the axial lip Sc and the groove side surface 6ab of the circumferential groove 6a.
  • a lip Sd that makes light contact with one groove side surface 6ab of the inner ring extension 6 may be provided at the tip of the suppression valve CS.
  • the suppression valve CS of this example has a base end portion Sa and a lip body SL.
  • a non-contact lip Sb extending radially inward and a light-contact lip Sd extending in the axial direction are branched and provided in an L-shaped cross section at the distal end portion of the lip body SL.
  • the base end portion of the lip body SL is thinner than the axial thickness t1 of the base end portion Sa, and is thicker than the thicknesses of the lips Sb and Sd.
  • the base end portion of the lip body SL is provided with two or more holes ha for supplying lubricating oil into the bearing space A1. These holes ha are arranged at equal intervals along the circumferential direction. However, it is also possible to arrange a plurality of holes ha at unequal intervals. The diameter dimension of each hole ha and the number of holes ha are determined by the amount of lubricating oil to be introduced into the bearing space A1.
  • the rolling bearing devices 28 and 28 according to the specific example of the application form can be applied in the same manner as the application example of the rolling bearing according to the first embodiment of the present invention shown in FIG. Since the suppression valve CS (FIG. 34) that suppresses the amount of lubricating oil that enters the shaft is provided, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.
  • the suppression valve CS FIG. 34

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
PCT/JP2012/072853 2011-09-22 2012-09-07 転がり軸受装置 WO2013042552A1 (ja)

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JP2011207723A JP5739293B2 (ja) 2011-09-22 2011-09-22 転がり軸受装置
JP2011-207723 2011-09-22
JP2011250448A JP5816061B2 (ja) 2011-11-16 2011-11-16 転がり軸受の潤滑装置
JP2011-250448 2011-11-16

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Cited By (4)

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CN111504507A (zh) * 2020-05-15 2020-08-07 辽宁东科电力有限公司 一种用于多支路环网柜一次接线同时完成温升试验装置及方法
CN113090572A (zh) * 2021-05-10 2021-07-09 中国航发湖南动力机械研究所 一种集成多功能的轴承外套
CN114829776A (zh) * 2019-12-20 2022-07-29 松下知识产权经营株式会社 涡旋式压缩机
WO2023201969A1 (zh) * 2022-04-21 2023-10-26 洛阳轴承研究所有限公司 隔圈组件及轴承组件

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JP6495700B2 (ja) * 2015-03-17 2019-04-03 Ntn株式会社 軸受装置および機械装置
TWI603020B (zh) 2016-11-04 2017-10-21 財團法人工業技術研究院 流體機械潤滑系統總成
TWI622716B (zh) * 2017-06-28 2018-05-01 Proth Industrial Co Ltd 液靜壓滑塊裝置
CN112648295B (zh) * 2019-10-09 2022-07-08 中国航发商用航空发动机有限责任公司 一种航空发动机的轴承组件及航空发动机

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JP2004332755A (ja) * 2003-04-30 2004-11-25 Ntn Corp 転がり軸受のエアオイル潤滑構造
JP2008075882A (ja) * 2007-12-11 2008-04-03 Nsk Ltd 軸受装置
JP2008082496A (ja) * 2006-09-28 2008-04-10 Ntn Corp 転がり軸受の潤滑装置

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JP2004332755A (ja) * 2003-04-30 2004-11-25 Ntn Corp 転がり軸受のエアオイル潤滑構造
JP2008082496A (ja) * 2006-09-28 2008-04-10 Ntn Corp 転がり軸受の潤滑装置
JP2008075882A (ja) * 2007-12-11 2008-04-03 Nsk Ltd 軸受装置

Cited By (4)

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Publication number Priority date Publication date Assignee Title
CN114829776A (zh) * 2019-12-20 2022-07-29 松下知识产权经营株式会社 涡旋式压缩机
CN111504507A (zh) * 2020-05-15 2020-08-07 辽宁东科电力有限公司 一种用于多支路环网柜一次接线同时完成温升试验装置及方法
CN113090572A (zh) * 2021-05-10 2021-07-09 中国航发湖南动力机械研究所 一种集成多功能的轴承外套
WO2023201969A1 (zh) * 2022-04-21 2023-10-26 洛阳轴承研究所有限公司 隔圈组件及轴承组件

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