WO2007129441A1 - Dispositif de roulement à plusieurs rangées - Google Patents

Dispositif de roulement à plusieurs rangées Download PDF

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Publication number
WO2007129441A1
WO2007129441A1 PCT/JP2007/000373 JP2007000373W WO2007129441A1 WO 2007129441 A1 WO2007129441 A1 WO 2007129441A1 JP 2007000373 W JP2007000373 W JP 2007000373W WO 2007129441 A1 WO2007129441 A1 WO 2007129441A1
Authority
WO
WIPO (PCT)
Prior art keywords
spacer
oil
inner ring
bearing
outer ring
Prior art date
Application number
PCT/JP2007/000373
Other languages
English (en)
Japanese (ja)
Inventor
Takashi Kawai
Mineo Koyama
Masatsugu Mori
Original Assignee
Ntn Corporation
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 JP2006127389A external-priority patent/JP2007298128A/ja
Priority claimed from JP2006337202A external-priority patent/JP5183059B2/ja
Application filed by Ntn Corporation filed Critical Ntn Corporation
Priority to DE112007001043T priority Critical patent/DE112007001043T5/de
Publication of WO2007129441A1 publication Critical patent/WO2007129441A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General buildup of machine tools, e.g. spindles, slides, actuators

Definitions

  • the present invention relates to a multi-row rolling bearing device that is configured by arranging a plurality of rolling bearings, and is used for supporting a spindle of a machine tool, etc. It relates to the lubrication of rotating bearings.
  • Machine tool spindles are becoming increasingly faster in order to increase machining efficiency. As the spindle speed increases, the torque and heat generation of the spindle bearing increase. To address this, jet lubrication and air-oil lubrication are often used to lubricate main shaft bearings.
  • Jet lubrication involves injecting a large amount of oil into a bearing to simultaneously lubricate the bearing and cool the bearing, but this lubrication method increases the stirring resistance of the lubricant when the bearing is operated at high speed. As a result (approximately proportional to the square of the speed), the power loss of the bearing increases, and there is a disadvantage that a large capacity drive motor is required.
  • air oil lubrication is a method in which lubricating oil is mixed with the carrier air and the oil is injected from the nozzle into the bearing.
  • a measure to reduce the agitation resistance of the oil in the bearing There has been proposed a method in which a small amount of oil is attached and oil is supplied to the raceway using centrifugal force and surface tension (for example, Japanese Patent Application Laid-Open No. 2 0 0 1 _ 0 1 2 4 8 1). Open 2 0 0 2 _ 5 4 6 4 3).
  • Lubrication devices that perform conventional air-oil lubrication have almost no bearing cooling effect, and there is a problem of heat generation of the bearing in applications of ultra-high speed rotation.
  • the present applicant has proposed Japanese Patent Laid-Open No. 2 0 06-1 1 8 5 2 5 as a lubricating device effective in solving such a cooling problem and rotating at an ultra high speed. If the proposed example is a multi-row rolling bearing device that is used in combination with the back of the fixed position preload, for example, on the spindle front side (fixed side), it is as shown in Fig. 13.
  • the outer ring spacer is a bearing lubrication spacer 58, and this shaft Lubricant is discharged from the nozzle 5 9 of the spacer 5 8 to the circumferential groove 5 7 on the width surface of the bearing inner ring 5 3, and the lubricating oil is discharged from the inner ring 5 3 by centrifugal force and surface tension. It leads to the raceway surface 5 3 a of the inner ring 5 3 along the inclined surface portion 5 3 b of the radial surface. Further, a flange-like portion 61 is provided on the slope portion 53b through a gap, and the lubricating oil flowing from the gap to the raceway surface 53a is guided.
  • the lubricating oil discharge path 62 is configured using an annular lid member 60 having a U-shaped cross section fitted to the inner diameter surface of each bearing lubrication spacer 58. That is, the lubricating oil discharge path 62 has a large diameter excluding the formation part of the nozzle 59 in the half part on the protruding side of the flange 61 in the axial direction, that is, the half part near the bearing 52 in the axial direction.
  • the stepped surface 58a and the axial flange 61 1 the half of the opposite side of the protruding side, that is, the half of the side away from the axial bearing 52, has a large diameter over the entire circumference.
  • Oil drain space 6 4 surrounded by the inner wall surface of the annular lid member 60 having a U-shaped cross-section to be fitted to the surface 5 8 b and the outer diameter surface of the inner ring spacer 6 7 in contact with the end surface of the inner ring 53 And an oil drain passage 6 3 that communicates the oil drain space 64 with the outside.
  • the oil drainage path 63 extends across the annular lid member 60 from the bearing lubrication spacer 58 at a position spaced circumferentially from the formation portion of the nozzle 59 in the bearing lubrication spacer 58. And are formed so as to penetrate in the radial direction.
  • Patent Document 1 Japanese Patent Laid-Open No. 2 0 0 1 _ 0 1 2 4 8 1
  • Patent Document 2 Japanese Patent Laid-Open No. 2 0 0 2 _ 5 4 6 4 3
  • Patent Document 3 Japanese Patent Laid-Open No. 2 0 0 6 _ 1 1 8 5 2 5
  • the width of the inner ring spacer 6 7 or the bearing lubrication spacers 5 8 and 5 8 is machined to match the difference in plane between the left and right rolling bearings 5 2 and 52.
  • the internal gap will be adjusted.
  • the bearing lubrication spacer 58 has a shape in which the flange 61 protrudes from one side surface in the axial direction, it is difficult to add the width surface. Therefore, the width of the inner ring spacer 6 7 is machined to adjust the axial internal clearance, but if the internal clearance is made smaller than intended, a new inner ring spacer 6 7 can be manufactured or used for bearing lubrication. The only way to process the width of the spacer 5 8 is.
  • spindle spindles used in machine tools are required to reduce the axial dimension as the machine becomes more compact. Therefore, the axial direction of a bearing lubrication spacer attached to the spindle is required. There is a need for reduced dimensions.
  • the object of the present invention is to secure a drainage path and cool the bearing, and can be applied to high-speed rotation, while reducing man-hours and costs by reducing the number of parts, and shaft
  • Another object of the present invention is to make the spindle spindle and the machine itself compact when applied to support of the spindle of a machine tool.
  • the rolling bearing device of the present invention is a multi-row rolling bearing device in which a plurality of rolling bearings are arranged, and a pair of bearing lubrication spacers are interposed between the outer rings of adjacent rolling bearings.
  • the spacer is a nozzle that discharges lubricating oil to the inner ring of the opposing rolling bearing and a flange that covers the outer circumference of the inner ring that is located on the outer diameter side of this nozzle.
  • An oil discharge space that communicates with each of the spaces from which the lubricating oil discharged from the nozzles in the adjacent rolling bearings is discharged has one of the following configurations (A) and (B): Yes.
  • the oil drainage space is formed between the pair of bearing lubrication spacers and the central outer ring spacer.
  • the oil drainage space is formed between the inner surface of the oil drain recess of these two bearing lubrication spacers and the outer diameter surface of the inner ring spacer.
  • the configuration (A) it is possible to supply the lubricating oil to the inside of the rolling bearing with the lubricating oil discharged from the nozzle of the bearing lubricating spacer.
  • the oil drainage space is formed between the single central outer ring spacer and the pair of bearing lubrication spacers, so that the oil drainage path for the lubricant discharged from the nozzle is secured and the bearing is cooled by the lubricant.
  • one central outer ring spacer is provided between the bearing lubrication spacers on both sides. There is no need to add an annular lid. Therefore, the alignment width of the bearing lubrication spacers can be narrowed, and the axial dimension can be reduced.
  • a single central outer ring spacer and a pair of bearing lubrication spacers sandwiching the central outer ring spacer are interposed between the outer rings of adjacent rolling bearings, so the width of the central outer ring spacer is adjusted.
  • the axial internal clearance can be easily adjusted with just this. Even if the oil drainage space is open to the outside and temporarily accumulates lubricating oil In addition, the lubricating oil may be kept stored.
  • an oil drain space is formed between both bearing lubrication spacers, and therefore, an oil drain path for lubricating oil discharged from the nozzles of the bearing lubrication spacers.
  • the bearing can be cooled with lubricating oil and can be applied to high-speed rotation and ultra-high-speed rotation.
  • a recess for oil drainage that opens to the inner peripheral surface is formed on the side of the contact side of both bearing lubrication spacers, and the inner surface of the oil drainage recess for these bearing lubrication spacers.
  • the space surrounded by the outer diameter surface of the inner ring spacer is used as the oil drainage space, there is no need to add another annular lid member for obtaining the lubricating oil discharge path as in the above-mentioned proposed example.
  • the structure of the oil drainage of the bearing lubrication spacer can be simplified, the number of parts can be reduced, man-hours and costs can be reduced.
  • the width of the spacers can be narrowed, and the axial dimension of the multi-row rolling bearing device can be reduced.
  • oil drainage recesses are formed on both surfaces of the single central outer ring spacer, and the oil drainage space is formed with the oil drainage recesses. You may form between the side surfaces of the said bearing lubrication spacer. With such a simple configuration, it is possible to secure an oil drainage route for the lubricant discharged from the nozzle.
  • the adjacent rolling interposes an inner ring spacer between inner rings of a re-bearing, and the oil drainage space is used for lubricating these bearings.
  • the oil drainage route for the lubricant discharged from the nozzle can be secured with a simple configuration.
  • the central outer ring spacer is preferably a ring having a rectangular cross section.
  • the pair of bearing lubrication spacers are formed on the inner peripheral side of one end and the other end in the axial direction of the central outer ring spacer.
  • the outer ring spacer has an oil drain recess on both sides, and the oil exhaust space is formed between the oil drain recess and the side surface of the bearing lubrication spacer. You may form between.
  • the bearing lubrication spacer and the central outer ring spacer can be made separate, and the rear side of the bearing lubrication spacer (the side facing the annular step) can be adjusted. Therefore, the gap between the outer diameter part of the inner ring and the collar part can be properly managed. By properly managing this gap, the lubricating oil will not flow into the bearing more than necessary. Therefore, it is possible to prevent an increase in the agitation resistance of the lubricating oil and to prevent the power loss of the bearing.
  • the bearing oil discharged from the nozzle of the bearing lubrication spacer allows the lubrication oil to be supplied to the inside of the rolling bearing, and the drainage recesses on both sides of the outer ring spacer
  • An oil drainage space is formed between the bearing lubrication spacer and the side surface of the bearing lubrication spacer, so that a lubricant drainage path is secured and cooling with the lubricant can be performed, making it possible to apply to high-speed rotation and ultra-high-speed rotation. . Since this oil drainage space is formed between the oil drainage recesses on both sides of the outer ring spacer and the side surfaces of the bearing lubrication spacer, it is necessary to add separate annular lid members to each bearing lubrication spacer.
  • the central outer ring spacer is arranged on the inner peripheral side of one end and the other end in the axial direction.
  • the outer diameter portion of the inner ring is provided with an inner ring inclined portion that increases in diameter from the end surface side of the inner ring toward the raceway surface side of the inner ring.
  • a bearing lubrication spacer may be provided on the stepped portion via an adjustment spacer that can adjust the gap between the inner ring inclined portion and the flange portion.
  • the adjustment spacer between the bearing lubrication spacer and the central outer ring spacer is processed and adjusted. can do.
  • the gap between the inner ring inclined portion and the flange portion can be managed appropriately and easily.
  • the multi-row rolling bearing device is a multi-row rolling bearing device that supports a main shaft of a machine tool, and the adjacent rolling bearings interposing the bearing lubrication spacer are fixed positions. It can also be used as a preload and rear combination.
  • FIG. 1 (A) is a cross-sectional view showing a multi-row rolling bearing device according to a first embodiment of the present invention.
  • (B) is an enlarged view of part A in FIG. 1 (A).
  • FIG. 2 is a sectional view showing a spindle device provided with the multi-row rolling bearing device.
  • FIG. 3 is a cross-sectional view showing a multi-row rolling bearing device according to a second embodiment of the present invention.
  • FIG. 4 is a sectional view showing a spindle device provided with the multi-row rolling bearing device.
  • FIG. 5 is a cross-sectional view showing a multi-row rolling bearing device according to a third embodiment of the present invention.
  • FIG. 6 is a cross-sectional view of the main part of the multi-row rolling bearing device.
  • FIG. 7 is a sectional view showing a spindle device provided with the multi-row rolling bearing device.
  • FIG. 8 is a cross-sectional view showing a multi-row rolling bearing device including an adjustment spacer according to a fourth embodiment of the present invention.
  • FIG. 9 is a cross-sectional view of a main part of the multi-row rolling bearing device.
  • FIG. 10 is a sectional view showing a spindle device provided with the multi-row rolling bearing device.
  • FIG. 11 (A) is a cross-sectional view showing a multi-row rolling bearing device according to a fifth embodiment of the present invention.
  • (B) is an enlarged view of a portion A in FIG. 11 (A).
  • FIG. 12 is a sectional view showing a spindle device provided with the multi-row rolling bearing device.
  • FIG. 13 is a cross-sectional view of the proposed example.
  • FIG. 1 (A) shows a cross-sectional view of the multi-row rolling bearing device of this embodiment.
  • This multi-row rolling bearing device 1 has a plurality (two in this case) of rolling bearings 2 arranged side by side.
  • Each rolling bearing 2 consists of an anguillare ball bearing, which is a rear combination and is used with fixed position preload.
  • Each rolling bearing 2 has a plurality of rolling elements 5 made of poles interposed between raceway surfaces 3 a and 4 a of the inner ring 3 and the outer ring 4, and each rolling element 5 is held by a cage 6. .
  • a center outer ring spacer 13 and a pair of bearing lubrication spacers 8 and 8 sandwiching the center outer ring spacer 13 are interposed.
  • An inner ring spacer 17 is interposed between the inner rings 3 and 3 of the adjacent rolling bearings 2 and 2.
  • the bearing lubrication spacer 8 discharges cooling oil and supplies a part of it to the rolling bearing 2 facing it.
  • the cage 6 is an outer ring guide type, and its material is preferably phenol resin, PEEK, PPS, polyamide resin, CZC composite, aluminum alloy, Ti alloy (improves strength at high speed).
  • the material of the inner ring 3 is, for example, carburized steel in consideration of the large fitting hoop stress at high speed.
  • the rolling element 5 is preferably made of ceramic from the viewpoint of reducing centrifugal force.
  • a circumferential groove 7 that is recessed in the axial direction is formed on the width surface of the inner ring 3 of each rolling bearing 2 on the side opposite to the load (bearing rear side). Further, the outer diameter surface following the raceway surface 3 a on the side where the circumferential groove 7 of the inner ring 3 is formed is a slope portion 3 b having a larger diameter on the raceway surface 3 a side. That is, the outer diameter surface of the portion where the step surface of the inner ring 3 is provided is the slope portion 3 b.
  • the bearing lubrication spacer 8 is in contact with the width surface of the opposed outer ring 4, so that the rolling bearing 2 This is a ring-shaped outer ring spacer provided adjacent to each other in the axial direction.
  • the bearing lubrication spacer 8 has a nozzle 9 that opens to face the portion where the circumferential groove 7 is provided on the width surface of the inner ring 3, and an oil supply passage 10 that communicates with the nozzle 9.
  • a buttocks 1 1 is provided.
  • the cooling oil supplied to the oil supply passage 10 and discharged from the nozzle 9 is blown to the circumferential groove 7 of the inner ring 3, and a part of it is centrifugal force and surface tension, and the slope from the inner diameter surface of the circumferential groove 7 Flows as lubricating oil along raceway 3a of inner ring 3 along 3b.
  • the flange portion 1 1 extends in the axial direction from one side surface of the bearing lubrication spacer 8 toward the opposing bearing 2, and has a clearance (5 (Fig. 1 (B)) and guides the lubricating oil flowing from the gap (5) to the raceway surface 3a.
  • the flange 11 extends to the inner diameter side of the cage 6.
  • the corner portion where the width surface of the inner ring 3 facing the nozzle 9 and the inclined surface portion 3b intersect with each other is a curved surface portion 3 ba having an arcuate cross section. This is to prevent the lubricating oil from leaving the inner ring 3 due to centrifugal force.
  • each bearing lubrication spacer 8 On the side surface of each bearing lubrication spacer 8 that is in contact with the central outer ring spacer 13 is formed an oil drain recess 8a that opens to the inner peripheral side. Further, the central outer ring spacer 13 has annular oil drain recesses 1 3 a on both surfaces, and the oil drain recesses on the side surfaces of the respective bearing lubrication spacers 8 facing the oil drain recesses 13 a. An oil drainage space 1 4 is formed between 8a and 8a. These oil drain spaces 14 are communicated with spaces 18 in which the lubricating oil discharged from the nozzle 9 in the rolling bearings 2 and 2 on both sides is discharged.
  • a groove-like oil drain passage 15 extending radially from the oil drain recess 13 a toward the outer peripheral side is provided at a portion of the central outer ring spacer 13 that contacts each bearing lubrication spacer 8 on both sides. Each is formed. Further, a groove-like oil drainage path 16 extending in the radial direction is also formed on a part of the side surface of each bearing lubrication spacer 8 that contacts the width surface of the outer ring 4.
  • the bearing lubrication spacer 8 is preferably hardened from the standpoint of preventing scratches and improving handling.
  • the lubricating oil discharge path 1 2 includes an oil drain recess 8 a formed on the side surface of the bearing lubrication spacer 8 and an oil drain recess 1 3 a formed on the side surface of the center outer ring spacer 1 3. And the grooved oil drainage passages 15 and 16 and the like. Note that a plurality of groove-like oil drain passages 15 and 16 may be provided in the circumferential direction.
  • the cooling oil used should have an ISO viscosity of VG 10 or VG 2 or less from the viewpoint of reducing power loss and improving cooling efficiency.
  • the use of water-soluble hydraulic fluid with low viscosity and high thermal conductivity as the cooling oil, and linear expansion coefficient as the material for the bearing lubrication spacer 8 are used. It is desirable to use low stainless steel.
  • the lubricating action of the multi-row rolling bearing device 1 having the above-described configuration will be described.
  • the cooling oil pumped to the oil supply passage 10 of each bearing lubrication spacer 8 is discharged from the nozzle 9 and sprayed to the location where the circumferential groove 7 is formed in the width surface of the inner ring 3 that faces it.
  • a part of the cooling oil sprayed on the circumferential groove 7 is caused by the surface tension and the centrifugal force acting on the cooling oil as the inner ring 2 rotates, so that the inner wall surface on the outer diameter side of the circumferential groove 1 in the inner ring 3
  • the oil flows into the raceway surface 3a of the inner ring 3 along the slope 3b as lubricating oil.
  • the cooling oil discharged from the nozzle 9 force is collected in the circumferential groove 1, and a part of it flows from the slope 3b of the inner ring 3 to the raceway surface 3a.
  • Lubricating oil can be supplied evenly all around. Lubricating oil moves smoothly from the inner wall surface of the circumferential groove 7 to the slope 3 b by properly balancing the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil, and the inclination angle of the slope 3 b. It is possible to prevent the lubricating oil from being scattered by centrifugal force.
  • the intersecting portion between the width surface of the inner ring 3 and the inclined surface portion 3 b is the curved surface portion 3 ba, the lubricating oil moves to the inclined surface portion 3 b more smoothly.
  • the inclined surface 3b of the inner ring 3 is covered with a gap (the flange 11 of the bearing lubrication spacer 8 through 5), and the lubricating oil flowing from the gap (5 to the raceway surface 3a) Gap (Lubricated oil flowing in 5 does not flow on the slope 3 b due to various conditions such as rotational speed and angle of inclination, but the action of centrifugal force.
  • Gap Low-Chip
  • the lubricating oil that flows in this state falls off the outer diameter side by centrifugal force at the point where it comes out of the tip of the flange 11.
  • the lubricating oil that has flowed down from the tip of the flange portion 11 to the outer diameter side is received by the inner diameter surface of the cage 6 and is rotated. It will be supplied to the moving body 5. For this reason, the gap between the inclined surface portion 3 b of the inner ring 3 and the flange portion 11 of the bearing lubrication spacer 8 (the lubricating oil supplied to 5 is used for lubrication without waste.
  • the flow rate can be adjusted with this gap (5.
  • the flow rate of the lubricating oil flowing through the minute gap (5) can be easily adjusted without adjusting the flow rate from the outside.
  • the remaining lubricating oil excluding the inflow flowing into the minute gap d is composed of the oil drain recess 13 on the side surface of the central outer ring spacer 13 and the oil drain recess on the side surface of the bearing lubrication spacer 8.
  • Lubricating oil space enclosed by a 1 4 grooved oil drainage passage 15 on the side of the central outer ring spacer 1 3, grooved oil drainage passage 1 6 on the side of the bearing lubrication spacer 8, etc. It is discharged to the outside by an oil discharge pump (not shown) through an oil discharge path 1 2.
  • the multi-row rolling bearing device 1 is effectively cooled by the lubricating oil as the cooling oil discharged through such a path.
  • FIG. 2 shows an example of a spindle device provided with the multi-row rolling bearing device 1 of the embodiment shown in FIG.
  • This spindle device 24 is applied to a machine tool, and a chuck of a tool or a workpiece is attached to the end of the main shaft 25 (the end on the left side in the figure).
  • the main shaft 25 is supported by a plurality (two in this case) of multi-row rolling bearing devices 1 separated in the axial direction.
  • the adjacent rolling bearings 2 and 2 with a central outer ring spacer 13 and a pair of bearing lubrication spacers 8 and 8 interposed are combined in the rear surface and fixed as described below. Used with preload.
  • each multi-row rolling bearing device 1 the inner ring 3 of the both rolling bearings 2 is fitted to the outer diameter surface of the main shaft 25, and the outer ring 4 is fitted to the inner diameter surface of the housing 26.
  • a motor 30 for driving the main shaft 25 is disposed at an intermediate position in the axial direction between the two-row rolling bearing devices 1 and 1 in the housing 26.
  • the motor rotor 31 is fixed to the main shaft 25, and the motor stator 3 2 is fixed to the housing 26.
  • the inner and outer rings 3, 4 of the rolling bearing 2 located on the spindle shaft end side in each multi-row rolling bearing device 1 are connected to the main shaft 25 and the housing 26 by the inner ring retainer 2 7 and the outer ring retainer 28. It is fixed in a sandwiched state between the step portions 25 a and 26 a facing in the axial direction.
  • a bearing fixing nut 3 3 that is pressed against the inner ring retainer 27 and that fixes the multi-row rolling bearing device 1 is screwed.
  • the housing 26 has a double structure including an inner peripheral housing 2 6 A and an outer peripheral housing 2 6 B.
  • the inner housing 2 6 A has a lubricating oil supply path 3 4 communicating with the bearing lubrication spacer 8, a lubricating oil supply path 3 4, an exhaust oil recovery path 3 5, and an oiling path 3 6 for cooling the housing. Is provided.
  • Each of the lubricating oil supply paths 3 4 and the exhaust oil recovery path 3 5 extends in the axial direction and penetrates the outer ring retainer 28.
  • the oil collecting path 35 is connected to a lubricating oil discharging path 12 (FIG. 1) of each bearing lubricating spacer 8.
  • the drained oil that has flowed out into the drained oil recovery passage 35 is collected in an oil recovery tank by a drain oil pump and returned to a cooling oil supply device (none of which is shown), and this cooling oil supply device Then, the cooling oil is supplied to the oil supply passage 10 again. Further, the cooling oil is also supplied from the cooling oil supply device to the oil supply path 36, and the housing 26 is cooled. The cooling oil that has cooled the housing 26 is recovered in the oil recovery tank and returned to the cooling oil supply device again.
  • the multi-row rolling bearing device 1 is used for supporting the main shaft 25 of the spindle device 24 of the machine tool, so that the central outer ring spacer 13 and the bearing lubrication spacer 8 are interposed.
  • the matching rolling bearings 2 and 2 are used with fixed position preload and back-to-back alignment, the axial dimension of the bearing lubrication spacer 8 can be reduced, so the spindle device 24 and the machine tool itself Can be made compact.
  • FIG. 3 is a cross-sectional view showing a second embodiment of the multi-row rolling bearing device of the present invention.
  • this multi-row rolling bearing device 1A is replaced with a pair of bearing lubrication instead of the central outer ring spacer 13 having oil drain recesses 13a and 13a on both surfaces. It uses a ring-shaped central outer ring spacer 13 A with a simple rectangular cross-section sandwiched between the outer periphery of the side spacers 8 and 8.
  • FIG. 4 shows an example of a spindle device including the multi-row rolling bearing device 1 A of the second embodiment shown in FIG.
  • This spindle device 24 A is applied to a machine tool, and a tool or workpiece chuck is attached to the end of a spindle 25.
  • the main shaft 25 is supported by a plurality (two in this case) of multi-row rolling bearing devices 1 A separated in the axial direction.
  • the rolling bearings 2 and 2 adjacent to each other with a central outer ring spacer 13 A and a pair of bearing lubrication spacers 8 and 8 are in a fixed position preload and combined with the rear surface. Used in.
  • the other configuration is the same as that of the spindle device 24 in FIG. Also in the case of this spindle device 24 A, since the axial dimension of the bearing lubrication spacer 8 can be reduced, the spindle device 24 A and the machine tool itself can be made compact.
  • FIG. 5 is a cross-sectional view showing a multi-row rolling bearing device according to a third embodiment of the present invention.
  • FIG. 6 is a cross-sectional view of the main part of the multi-row rolling bearing device. This will be described with reference to FIG. In the following description, parts corresponding to the matters described in the preceding forms in each form may be denoted by the same reference numerals, and overlapping description may be omitted. When only a part of the configuration is described, the rest of the configuration is the same as the preceding form. [0044]
  • This multi-row rolling bearing device 1B has a plurality (two in this case) of rolling bearings 2 arranged side by side.
  • Each rolling bearing 2 consists of an anguillare ball bearing, which is a rear combination and is used with fixed position preload. Between the outer rings 4 and 4 of the adjacent rolling bearings 2 and 2, an outer ring spacer 3 7 serving as a central outer ring spacer is interposed, and between the inner rings 3 and 3 of the adjacent rolling bearings 2 and 2, An inner ring spacer 17 is interposed.
  • annular stepped portion 38 is formed on the inner peripheral side of one end and the other end in the axial direction of the outer ring spacer 37.
  • the amount of depression h 1 from one axial step of one annular stepped portion 3 8, and the amount of depression h 2 from the other axial end of the other annular stepped portion 3 8 are formed to have substantially the same amount.
  • the diameter dimensions 01 1 and d 2 of the one and the other annular step portions 38 and 38 are also formed to have substantially the same dimensions.
  • the diameter of each annular step portion 3 8 is formed to be larger than the inner diameter of the outer ring of the adjacent rolling bearings 2 and 2. In some cases, the two dents h 1 and h 2 of the annular step portions 3 8 and 3 8 are not substantially the same. In some cases, the diameters d 1 and d 2 of the annular step portions 3 8 and 3 8 are not substantially the same.
  • a pair of bearing-lubricating spacers 8 A and 8 A are fitted into these annular stepped portions 3 8 and 3 8 of the outer ring spacer 37, and are fixed by a plurality of ports 39.
  • Each bearing spacer 8 A has a plurality of port holes 8 A a formed along the axial direction at regular intervals in the circumferential direction (not necessarily at regular intervals).
  • a plurality of internal threads communicating with A a are formed in the outer ring spacer 37.
  • Each port hole 8 A a is provided with port 39 and is screwed into the corresponding female screw. The screwed Porto head is accommodated in the annular step portion 38 and does not interfere with the adjacent bearing 2.
  • the radius of the corner 3 8 R of the annular stepped portion 3 8 is made smaller than, for example, the chamfer dimension of the fitting portion 40 described later, and the annular stepped portion 3 8 and bearing lubrication The mating surface with the spacer 8 A comes into close contact.
  • the present invention is not limited to such a configuration, and a relief process or the like in which the annular step portion 38 and the bearing lubricating spacer 8A do not interfere with each other may be performed at the corner portion of the annular step portion 38.
  • the bearing lubrication spacer 8 A fitted into each annular step 3 8 of the outer ring spacer 3 7 has one axial direction and one axial direction other. Since they have the same symmetrical structure, only one axial direction will be described, and the other axial direction may be given the same reference numerals and explanation thereof may be omitted.
  • One bearing lubrication spacer 8A in the axial direction is formed with the above-mentioned port hole 8Aa, a fitting portion 40 fitted into the annular step portion 38, and a circumferential groove on the end face of the inner ring 3.
  • 7 has a nozzle 9 that opens to face a portion provided with 7, and a first oil supply passage 1 O a that communicates with the nozzle 9, and a flange portion 11 is provided.
  • the first oil supply passage 1 O a extends along a radial direction orthogonal to the axial direction, and is formed to open outward in the radial direction of the fitting portion 40.
  • the outer ring spacer 37 has a second oil supply path 10 Ob that communicates with the first oil supply path 10a and supplies cooling oil.
  • the cooling oil supplied to the second oil supply passage 1 Ob and discharged from the nozzle 9 is blown to the circumferential groove 7 of the inner ring 3, and a part thereof is centrifugal force and surface tension. From the inner diameter surface, flows along the slope portion 3 b as the lubricating oil to the raceway surface 3 a of the inner ring 3.
  • the flange portion 1 1 extends in the axial direction from one side surface of the bearing lubrication spacer 8A toward the opposite bearing 2, and a clearance S (Fig. 1 (B ), And the lubricating oil flowing from the gap S to the raceway surface 3a is guided.
  • the flange portion 11 is located on the outer diameter side of the nozzle 9 and extends to the inner diameter side of the cage 6.
  • an oil drainage recess 8Ab opened on the inner peripheral side is formed on the side surface of the outer ring spacer 37 that faces the annular stepped portion 38. Yes.
  • the outer ring spacer 3 7 has annular oil recesses 3 7 b on both surfaces of the wall portion 3 7 a on the inner diameter side of the annular step portion 38 and near the middle in the width direction of the outer ring spacer 37.
  • An oil drain space 4 1 is formed between these annular oil drain recesses 3 7 b and 3 7 b and oil bearing recesses 8 A b on the side surfaces of the respective bearing lubrication spacers 8 A.
  • the groove-like oil drainage passage 42 is a radially outer space 43 of the fitting portion 40 and communicates with the radially outer space 43 in the same phase as the one circumferential direction. Further, the groove-like oil drainage path 42 is formed in a radially outer space 43 of the fitting portion 40 and an annular space 40 facing the inner diameter side portion of the end face of the outer ring 4 in the fitting portion 40. communicate with a. It is desirable to quench the bearing lubrication spacer 8 A from the viewpoint of preventing scratches and improving handling.
  • the remaining lubricating oil excluding the inflow flowing into the minute gap ⁇ , takes away the heat of the inner ring 3 that generates heat during operation, and discharges the lubricating oil. It is discharged to the outside from the route.
  • This lubricating oil discharge path consists of an annular space 40 0 a of the fitting portion 40, a radially outer space 4 3 of the fitting portion 40, and a drainage recess 8 A b on the side surface of the bearing lubrication spacer 8 A , And an annular oil recess 3 7 b of the outer ring spacer 37.
  • the radially outer space 43 of the fitting portion 40 and the oil drainage recess 8Ab on the side surface of the bearing lubrication spacer 8A may be provided in a plurality distributed in the circumferential direction. .
  • the cooling oil that has been pressure-fed to the second oil supply passage 1 Ob of the outer ring spacer and supplied to the first oil supply passage 10 a of one and the other bearing lubrication spacers 8A and 8A is discharged from the nozzle 9.
  • a part of this sprayed cooling oil is caused by the surface tension and the centrifugal force acting on the cooling oil as the inner ring 2 rotates, from the inner wall surface on the outer diameter side of the circumferential groove 7 in the inner ring 3 to the slope portion 3 b. And flows into the raceway surface 3a of the inner ring 3 as lubricating oil.
  • the cooling oil discharged from the nozzle 9 is collected in the circumferential groove 7, and a part thereof flows from the slope portion 3b of the inner ring 3 to the raceway surface 3a.
  • Lubricating oil can be supplied evenly.
  • Lubricating oil moves smoothly from the inner wall surface of the circumferential groove 7 to the slope 3b by properly balancing the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil, and the inclination angle of the slope 3b. Can be carried out by the centrifugal force It is possible to avoid the splashing of lubricating oil.
  • the intersection of the width surface of the inner ring 3 and the inclined surface portion 3 b is the curved surface portion 3 ba, the lubricating oil moves to the inclined surface portion 3 b more smoothly.
  • the gap between the slope 3 b of the inner ring 3 and the flange 1 1 (from 5 the lubricating oil flowing to the raceway surface 3 a is guided by the flange 1 1.
  • the gap (the lubricating oil flowing in 5 May flow in a state of being pressed against the inner surface of the flange 11 by the action of centrifugal force, instead of being attached to the inclined surface 3 b due to various conditions such as rotational speed and inclination angle.
  • the lubricating oil that flows in this state drops off to the outer diameter side by centrifugal force at the point where it protrudes from the tip of the flange part 11.
  • the flange part 11 extends to the inner diameter side of the cage 6.
  • the lubricating oil that has flowed down from the tip of the flange 11 to the outer diameter side is received by the inner diameter surface of the cage 6 and supplied to the rolling elements 5. Therefore, the inclined surface portion of the inner ring 3 3 Clearance between bearing b and bearing flange spacer 8 A 1 1 (The lubricating oil supplied to 5 is used for lubrication without waste. The remaining lubricating oil, excluding the inflow that flows into the space S, is discharged to the outside through the lubricating oil discharge path by an unillustrated drain pump, etc. Lubricating as cooling oil discharged through such a path The multi-row rolling bearing device 1 B is effectively cooled by the oil.
  • the outer ring spacer 3 7 is interposed between the outer rings 4, 4 of the adjacent rolling bearings 2, 2.
  • An annular step portion 3 8 is formed on the inner peripheral side of one end and the other end of the outer ring spacer 3 7 in the axial direction, and a pair of bearing lubricating spacers 8 A and 8 A are connected to the annular step portions 3 8 and 3. 8 is inserted in each. Therefore, it is possible to easily adjust the width dimension 3 7 h by polishing the width face of the outer ring spacer 37.
  • the processing method of the width surface of the outer ring spacer 37 is not limited to polishing, and for example, a processing method such as turning or superfinishing may be used as necessary.
  • the bearing lubrication spacer 8 A has a configuration in which the flange 11 protrudes from the one side surface in the axial direction, but the bearing lubrication spacer 8 A is removed from the outer ring spacer 3 7.
  • the width surface of the outer ring spacer 37 can be processed. Yo Accordingly, the width surface of the outer ring spacer 37 can be easily processed without being interfered by the flange 11.
  • the axial internal clearance of the bearings 2 and 2 can be easily adjusted simply by adjusting the width dimension 3 7 h etc. of the outer ring spacer 3 7.
  • the bearing lubrication spacer 8A and the outer ring spacer 3 7 are separated, the back side of the bearing lubrication spacer 8A (the side facing the annular step portion 3 8), or The ring-shaped step 3 8 of the outer ring spacer 3 7 can be processed and adjusted. Accordingly, an inner ring inclined portion 3 b formed on the outer diameter portion of the inner ring 3, and an inner ring inclined portion 3 b that increases in diameter from the end surface side of the inner ring 3 toward the raceway surface side of the inner ring 3, The clearance between the flange portion 1 1 (5 can be properly managed.
  • the adjustment of the axial internal clearance, the inner ring inclined portion 3 b, The clearance between the flange 1 and 1 (5 can be adjusted independently, so the number of man-hours can be reduced compared to the axial internal clearance and the clearance that is adjusted almost simultaneously. Monkey.
  • the gap (5 is too small, and the slope 3b of the inner ring 3 interferes with the flange 1 1 due to the mounting condition when the bearing is installed, expansion of the inner ring 3 due to heat generation, centrifugal force, etc. Can also be prevented.
  • the first and second oil passages 1 O a and 1 Ob may be formed. Also in this case, misalignment of the first and second oil passages 1 O a and 10 b can be reliably prevented. Accordingly, the cooling oil can be smoothly supplied to the first and second oil passages 10 a and 10 b.
  • a bearing lubrication spacer is provided on the annular step portion 3 8 formed on the inner peripheral side of the outer ring spacer 37.
  • the partial end surface 3 7 c of the outer ring spacer 3 7 is formed in the same plane as the step surface portion 3 8 a from one circumferential direction of the step surface portion 3 8 a forming the annular step portion 3 8, that is, flush with the surface. Notches are formed on the surface. Therefore, for example, the partial end surface 37c can be rapidly processed using the stepped surface portion 38a as a processing reference surface, so that the number of processing steps can be reduced.
  • the radial outer space 4 3 of the fitting part 40 and the grooved oil drainage path 42 can be processed simultaneously, for example by milling, so the man-hours for the setup change are reduced. Can be reduced.
  • the weight of the outer ring spacer 37 can be reduced, and the drained oil can be discharged more smoothly from the radially outer space 43 and the like.
  • the outer ring spacer 37 has annular drain recesses 37b on both surfaces of the wall 37a near the middle in the axial direction. Since the annular oil drain recess 3 7 b is formed, the wall portion 3 7 a near the middle in the axial direction of the outer ring spacer 37 can be formed into a thin structure.
  • the outer ring spacer 37 is formed by forming the radially outer space 43 and reducing the weight of the outer ring spacer 37 by forming a thin wall structure 37a near the middle in the axial direction. The handling can be facilitated.
  • a lubricant drain space 4 1 is secured between the recesses 3 7 b for oil drainage on both sides of the outer ring spacer 3 7 and the side surface of the bearing lubrication spacer 8 A for lubrication. It can be cooled with oil and applied to high-speed rotation and ultra-high-speed rotation.
  • This oil drainage space 41 is formed between the oil drainage recesses 3 7 b on both sides of the outer ring spacer 3 7 and the side surface of the bearing lubrication spacer 8 A. Therefore, each bearing lubrication spacer 8 A Therefore, it is not necessary to add a separate annular lid member, and the axial dimension of the bearing lubrication spacer 8A can be reduced.
  • FIG. 7 shows an example of a spindle device 2 4 B provided with the multi-row rolling bearing device 1 B of the third embodiment shown in FIGS. 5 and 6.
  • This spindle device 24 B is applied to a machine tool, and a tool or workpiece chuck is attached to the end of the spindle 25 on the tip side (the end on the left side in the figure).
  • the main shaft 25 is supported by a plurality (two in this case) of multi-row rolling bearing devices 1 B separated in the axial direction.
  • the adjacent rolling bearings 2 and 2 with the outer ring spacer 37 interposed therebetween are used in combination with the back and fixed position preload.
  • the inner ring 3 in each row is fitted to the outer diameter surface of the main shaft 25, and the outer ring 4 is fitted to the inner diameter surface of the housing 26.
  • a motor 30 that drives the main shaft 25 is disposed at an intermediate position in the axial direction between the two-row rolling bearing devices 2 and 2 in the housing 26.
  • the motor rotor 31 is fixed to the main shaft 25, and the motor stator 3 2 is fixed to the housing 26.
  • each multi-row rolling bearing device 1B The inner and outer rings 3 and 4 of the rolling bearing 2 located on the spindle shaft end side in each multi-row rolling bearing device 1B are connected to the main shaft 2 5 and the housing 26 by the inner ring retainer 2 7 and the outer ring retainer 28. It is fixed in a state of being sandwiched between the step portions 25 a and 26 a facing in the axial direction.
  • a bearing fixing nut 33 that presses against the inner ring retainer 27 and fixes the multi-row rolling bearing device 1 B is screwed to one end of the main shaft 25. Set the bearing contact surfaces of the main shaft 2 5 and the steps 2 5 a and 2 6 a of the housing 2 6 and even the inner ring presses 2 7 and the outer ring pressers 2 8 to the predetermined positions. By tightening 3, two rolling bearings 2 are in place. Preloaded.
  • the adjacent rolling bearings 2 and 2 interposing the outer ring spacer 3 7 are back-aligned with a fixed position preload. Since the bearing lubrication spacer 8A is fitted into the annular stepped portion 3 8 of the outer ring spacer 37, the axial dimension of the entire spacer can be reduced. 2 4 and the machine tool itself can be made compact.
  • FIG. 8 is a cross-sectional view showing a multi-row rolling bearing device according to the fourth embodiment of the present invention.
  • FIG. 9 is a cross-sectional view of the main part of the multi-row rolling bearing device.
  • this multi-row rolling bearing device 1 C is provided between the inner ring inclined portion 3 b and the flange portion 11 in the annular step portion 3 8 of the outer ring spacer 37.
  • a minute clearance (Adjustment spacer 4 A that can adjust 5 is provided with a bearing lubrication spacer 8 A. In other words, the adjustment spacer 4 4 is added.
  • a through hole 44a along the axial direction is formed in the seat 44, and the port 39 is inserted into the through hole 44.
  • the screwed Porto head is an annular step 3 8 is housed in the adjacent bearing 2 does not interfere.
  • the adjustment provided between the back surface 8 A c of the bearing lubrication spacer 8 A and the annular step portion 3 8 of the outer ring spacer 3 7. Process and adjust at least one of the one surface part and the other surface part of the spacer 4 4 by polishing or the like.
  • the minute gap S between the inner ring inclined portion 3 b and the flange portion 1 1 can be managed appropriately and easily.
  • the adjustment spacer 4 4 can be processed and adjusted. it can. In this manner, the minute gap (5 can be managed appropriately and easily.
  • the minute gap (adjustment of 5 can be adjusted). It is possible to reduce the assembly man-hours quickly by preparing adjustment spacers 4 with multiple adjustment widths 4 4 to adjust the minute gap (5 can be adjusted). Therefore, the outer ring spacer 3 7 and the bearing lubrication spacer 8 A are highly versatile and compatible. Can be achieved. Therefore, the manufacturing cost of the multi-row rolling bearing device 1 C can be reduced.
  • the other configuration is the same as the re-bearing device 1B in the multi-row rolling shown in FIG. 5 and FIG. 6, and has the same operations and effects.
  • FIG. 10 shows an example of a spindle device 24 C provided with the multi-row rolling bearing device 1 C shown in FIG. 8 and FIG.
  • This spindle device 24 C is applied to a machine tool, and a tool or workpiece chuck is attached to the end of a spindle 25.
  • the main shaft 25 is supported by a plurality (two in this case) of multi-row rolling bearing devices 1 C separated in the axial direction.
  • the adjacent rolling bearings 2 and 2 with the outer ring spacer 37 interposed therebetween are used in a fixed position preload and in combination with the back surface.
  • the other configuration is the same as that of the spindle device 24 B in FIG.
  • FIG. Fig. 11 (A) shows a cross-sectional view of the multi-row rolling bearing device of this embodiment.
  • This multi-row rolling bearing device 1 D is composed of a plurality (two in this case) of rolling bearings 2 arranged side by side.
  • Each rolling bearing 2 consists of an anguillare ball bearing, is combined with the back side, and is used with fixed position preload.
  • Each rolling bearing 2 has a plurality of rolling elements 5 made of poles interposed between raceway surfaces 3 a and 4 a of the inner ring 3 and the outer ring 4.
  • Each rolling element 5 is held by a cage 6.
  • a pair of bearing spacers 8 and 8 are interposed between the outer rings 4 and 4 of the adjacent rolling bearings 2 and 2.
  • An inner ring spacer 17 is interposed between the inner rings 3 and 3.
  • the bearing lubrication spacer 8 discharges cooling oil and supplies a part thereof into the corresponding rolling bearing 2.
  • the cage 6 is an outer ring guide type, and its material is preferably phenol resin, PEEK, PPS, polyamide resin, CZC composite, aluminum alloy, Ti alloy (improvement of strength at high speed).
  • the material of inner ring 3 is a large fit at high speed Considering the mating hoop stress, for example, carburized steel.
  • the rolling element 5 is preferably made of ceramic from the viewpoint of reducing centrifugal force.
  • a circumferential groove 7 that is recessed in the axial direction is formed on the width surface of the inner ring 3 on the anti-load side (bearing rear side) of each rolling bearing 2. Further, the outer diameter surface following the raceway surface 3 a on the side where the circumferential groove 7 of the inner ring 3 is formed is a slope portion 3 b having a larger diameter on the raceway surface 3 a side. That is, the outer diameter surface of the portion where the step surface of the inner ring 3 is provided is the slope portion 3 b.
  • the bearing-lubricating spacer 8 is a ring-shaped outer ring spacer provided adjacent to the rolling bearing 2 in the axial direction by coming into contact with the corresponding width surface of the outer ring 4.
  • This bearing lubrication spacer 8 has a nozzle 9 that opens to face the portion where the circumferential groove 7 is provided on the width surface of the inner ring 3, and an oil supply passage 10 that communicates with the nozzle 9.
  • a state part 1 1 is provided.
  • the cooling oil supplied to the oil supply passage 10 and discharged from the nozzle 9 is blown to the circumferential groove 7 of the inner ring 3, and a part of the cooling oil is inclined from the inner surface of the circumferential groove 7 by centrifugal force and surface tension. It flows as lubricating oil along raceway 3a of inner ring 3 along part 3b.
  • the bowl-shaped portion 1 1 extends in the axial direction from the side surface of the bearing lubrication spacer 8 toward the corresponding bearing 2, and has a clearance S (see FIG. 11 (B)) in the slope portion 3b of the inner ring 3. In this way, the lubricating oil flowing from the gap S to the raceway surface 3a is guided.
  • the hook-like portion 11 extends to the inner diameter side of the cage 6.
  • a corner portion where the width surface of the inner ring 3 facing the nozzle 9 and the slope portion 3 b intersect with each other is a curved surface portion 3 ba having an arcuate cross section. The reason why the curved surface portion 3 ba is used is to prevent the lubricating oil from leaving the inner ring 3 due to centrifugal force from the corner portion.
  • Groove-shaped oil drain passages 8 b extending in the radial direction from the portion 8 a toward the outer peripheral side are formed. Further, a groove-like oil drain passage 16 extending in the radial direction is also formed on a part of the side surface of each bearing lubrication spacer 8 that contacts the width surface of the outer ring 4. It is desirable to quench the bearing lubrication spacer 8 from the viewpoint of preventing scratches and improving handling.
  • the lubricating oil discharge path 12 includes an oil discharge space 14 B formed of a drain oil recess 8 a formed in the double bearing lubrication spacer 8, the grooved oil discharge paths 8 b, 16, etc. Consists of.
  • the groove-like oil drain passages 8b, 16 may be provided in a distributed manner in the circumferential direction.
  • the viscosity of ISO is preferably V G 10 or V G 2 or less from the viewpoint of reducing power loss and improving cooling efficiency.
  • the lubricating action of the multi-row rolling bearing device 1D configured as described above will be described.
  • the cooling oil pumped to the oil supply passage 10 of each bearing lubrication spacer 8 is discharged from the nozzle 9 and sprayed to the location where the circumferential groove 7 is formed in the width surface of the inner ring 3 that is opposed.
  • a part of the cooling oil sprayed on the circumferential groove 7 is caused by the inner surface of the inner ring 3 on the outer diameter side of the circumferential groove 7 due to the surface tension and the centrifugal force acting on the cooling oil as the inner ring 2 rotates.
  • the lubricant flows from the wall surface into the raceway surface 3a of the inner ring 3 along the slope portion 3b.
  • the cooling oil discharged from the nozzle 9 is collected in the circumferential groove 7, and a part thereof flows from the inclined surface portion 3b of the inner ring 3 to the raceway surface 3a, so that the entire circumference of the raceway surface 3a is obtained.
  • Lubricant can be supplied evenly.
  • Lubricating oil moves smoothly from the inner wall surface of the circumferential groove 7 to the slope 3b by appropriately balancing the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil, and the inclination angle of the slope 3b. It is possible to prevent the lubricating oil from being scattered by centrifugal force.
  • the intersection of the width surface of the inner ring 3 and the slope portion 3 b is the curved surface portion 3 ba, the lubricating oil moves more smoothly to the slope portion 3 b. To be done.
  • the slanted portion 3b of the inner ring 3 is covered with the flange portion 11 of the bearing lubrication spacer 8 through the gap S, and the lubricating oil flowing from the gap S to the raceway surface 3a has a bowl shape. Guided by part 1 1. Gap (Lubricated oil flowing in 5 does not flow on the inclined surface 3 b due to various conditions such as rotational speed and inclination angle. The lubricating oil that flows in this state will flow down to the outer diameter side by centrifugal force at the point where it exits the tip of the bowl-shaped part 10.
  • the hook-shaped part 11 extends to the inner diameter side of the cage 6, the lubricating oil that has flowed down from the tip of the hook-shaped part 11 to the outer diameter side is received by the inner diameter surface of the cage 6, and the rolling element Therefore, the gap between the slope 3 b of the inner ring 3 and the flanged portion 1 1 of the bearing lubrication spacer 8 (the lubricating oil supplied to 5 is lubricated without waste. Will be served.
  • the flow rate can be adjusted by the gap S, so the flow rate of the cooling oil to the oil supply passage 10 is The flow rate of the lubricating oil flowing through the minute gap S can be easily adjusted without adjusting from the outside.
  • the remaining lubricating oil excluding the inflow flowing into the minute gap 5 is a lubricating oil discharge path.
  • each bearing lubrication It is discharged to the outside by a drainage pump (not shown) through the grooved drainage passages 8b, 16 of the spacer 8 for use.
  • the multi-row rolling bearing device 1D is effectively cooled by the lubricating oil as the cooling oil discharged through such a path.
  • oil drainage recesses 8a that open to the inner peripheral surface are formed on the side surfaces of the both bearing lubrication spacers 8 and 8 that are in contact with each other.
  • the space surrounded by the inner surfaces of these oil drain recesses 8a, 8a and the outer diameter surface of the inner ring spacer 17 is referred to as oil drain space 14 B.
  • the lubricating oil discharge path 1 2 is configured to communicate with the space 18 from which the lubricating oil discharged from the nozzle 9 is discharged.
  • FIG. 12 shows an example of a spindle device provided with the multi-row rolling bearing device 1 D of the fifth embodiment shown in FIG.
  • This spindle device 24 D is applied to a machine tool, and a tool or workpiece chuck is attached to the tip of the main shaft 25 (the left end in the figure).
  • the main shaft 25 is supported by a plurality (two in this case) of multi-row rolling bearing devices 1 D separated in the axial direction.
  • the rolling bearings 2 and 2 adjacent to each other with a bearing lubrication spacer 8 interposed therebetween are combined on the back side and used in a fixed position preload as described later.
  • each multi-row rolling bearing device 1 D the inner ring 3 of the double rolling bearing 2 is fitted to the outer diameter surface of the main shaft 25, and the outer ring 4 is fitted to the inner diameter surface of the housing 26.
  • a motor 30 for driving the main shaft 25 is disposed at an intermediate position in the axial direction sandwiched between both the multi-row rolling bearing devices 1 D and 1 D in the housing 26.
  • the motor rotor 3 1 is fixed to the main shaft 25, and the motor stator 3 2 is fixed to the housing 26.
  • each multi-row rolling bearing device 1D The inner and outer rings 3 and 4 of the rolling bearing 2 located on the spindle shaft end side in each multi-row rolling bearing device 1D are connected to the main shaft 2 5 and the housing 26 by the inner ring retainer 2 7 and the outer ring retainer 2 8 respectively. It is fixed in a state of being sandwiched between the step portions 25 a and 26 a facing in the axial direction.
  • a bearing fixing nut 33 that presses against the inner ring retainer 27 and fixes the multi-row rolling bearing device 1 D is screwed to one end of the main shaft 25. Set the bearing contact surfaces of the main shaft 2 5 and the steps 2 5 a and 2 6 a of the housing 2 6 and even the inner ring presses 2 7 and the outer ring pressers 2 8 to the predetermined positions.
  • the housing 26 has a double structure composed of an inner peripheral housing 26 A and an outer peripheral housing 26 B.
  • the inner housing 2 6 A has a lubricating oil supply path 3 4 communicating with the bearing lubrication spacer 8, a lubricating oil supply path 3 4, an exhaust oil recovery path 3 5, and an oiling path 3 6 for cooling the housing. Is provided.
  • Each lubricating oil supply path 34 extends in the axial direction and opens at both end faces of the inner peripheral housing 26 A.
  • the oil recovery path 3 5 extends in the axial direction and penetrates the outer ring retainer 28.
  • a lubricating oil discharge path 12 (FIG. 11) of each bearing lubrication spacer 8 communicates with the oil recovery path 35.
  • the waste oil that has flowed out into the waste oil recovery path 35 is recovered in an oil recovery tank by a drain oil pump, and returned to a cooling oil supply device (none of which is shown).
  • This cooling oil supply device Then, the cooling oil is supplied to the oil supply passage 10 again. Further, the cooling oil is also supplied from the cooling oil supply device to the oil supply path 36, and the housing 26 is cooled.
  • the cooling oil that has cooled the housing 26 is recovered in the oil recovery tank and returned to the cooling oil supply device again.
  • the above-mentioned multi-row rolling bearing device 1D is used to support the spindle 25 of the machine tool 4 4 and the spindle 25 of the D, and the adjacent rolling bearing 8 with the bearing lubrication spacer 8 interposed therebetween is re-bearing 2.
  • 2 can be used at a fixed position and back-to-back, the axial dimension of the bearing lubrication spacer 8 can be reduced, so the spindle device 2 4 D and the machine tool itself can be made compact. It becomes possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un dispositif de roulement à plusieurs rangées comportant de multiples roulements disposés côte à côte. Une paire d'entretoises pour la lubrification des roulements est disposée entre les bagues extérieures des roulements adjacents et chaque entretoise comporte une buse pour déverser de l'huile de graissage sur la bague intérieure du roulement d'en face, ainsi qu'un rebord placé sur le côté du diamètre extérieur de la buse et surplombant le périmètre extérieur de la bague intérieure. Chacun des roulements adjacents comporte un espace dans lequel se déverse l'huile de graissage provenant de la buse et un espace d'écoulement d'huile en communication avec ledit espace est aménagé soit entre chaque paire d'entretoises pour la lubrification des roulements et une entretoise de bague extérieure centrale unique (structure (A)), soit entre la surface intérieure d'un évidement d'écoulement d'huile, qui est pratiqué dans une face latérale du côté de contact de chacune des paires d'entretoises pour la lubrification des roulements afin d'être ouvert vers la surface périmétrique intérieure, et la surface de diamètre extérieur d'une entretoise de bague intérieure disposée entre les bagues intérieures des roulements adjacents (structure (B)).
PCT/JP2007/000373 2006-05-01 2007-04-06 Dispositif de roulement à plusieurs rangées WO2007129441A1 (fr)

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JP2006-127388 2006-05-01
JP2006127389A JP2007298128A (ja) 2006-05-01 2006-05-01 多列転がり軸受装置
JP2006127388 2006-05-01
JP2006-127389 2006-05-01
JP2006337202A JP5183059B2 (ja) 2006-05-01 2006-12-14 多列転がり軸受装置
JP2006-337202 2006-12-14

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018091025A1 (fr) * 2016-11-15 2018-05-24 Schaeffler Technologies AG & Co. KG Pièce d'alimentation en lubrifiant
EP3783240A4 (fr) * 2018-08-31 2021-07-21 Gree Green Refrigeration Technology Center Co., Ltd. of Zhuhai Ensemble palier et compresseur doté dudit ensemble

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4986812B2 (ja) 2007-11-07 2012-07-25 Ｎｔｎ株式会社 主軸装置の間座製作方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06235425A (ja) * 1993-02-08 1994-08-23 Nippon Seiko Kk 軸受装置
JPH0988986A (ja) * 1995-09-27 1997-03-31 Ntn Corp アンギュラ玉軸受の潤滑冷却方法および装置
JP2000249151A (ja) * 1998-12-28 2000-09-12 Nsk Ltd 転がり軸受の潤滑構造
JP2002061657A (ja) * 2000-05-31 2002-02-28 Ntn Corp 転がり軸受のエアオイル潤滑構造
JP2004360828A (ja) * 2003-06-05 2004-12-24 Ntn Corp 転がり軸受の潤滑装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001012481A (ja) 1999-06-28 2001-01-16 Nsk Ltd 軸受装置
JP4261083B2 (ja) 2000-05-31 2009-04-30 Ｎｔｎ株式会社 転がり軸受のエアオイル潤滑構造
JP2006118525A (ja) 2004-10-19 2006-05-11 Ntn Corp 転がり軸受の潤滑装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06235425A (ja) * 1993-02-08 1994-08-23 Nippon Seiko Kk 軸受装置
JPH0988986A (ja) * 1995-09-27 1997-03-31 Ntn Corp アンギュラ玉軸受の潤滑冷却方法および装置
JP2000249151A (ja) * 1998-12-28 2000-09-12 Nsk Ltd 転がり軸受の潤滑構造
JP2002061657A (ja) * 2000-05-31 2002-02-28 Ntn Corp 転がり軸受のエアオイル潤滑構造
JP2004360828A (ja) * 2003-06-05 2004-12-24 Ntn Corp 転がり軸受の潤滑装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018091025A1 (fr) * 2016-11-15 2018-05-24 Schaeffler Technologies AG & Co. KG Pièce d'alimentation en lubrifiant
EP3783240A4 (fr) * 2018-08-31 2021-07-21 Gree Green Refrigeration Technology Center Co., Ltd. of Zhuhai Ensemble palier et compresseur doté dudit ensemble
US11802589B2 (en) 2018-08-31 2023-10-31 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Bearing assembly and compressor with bearing assembly

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