WO2019188621A1 - Structure de refroidissement pour dispositif de palier - Google Patents

Structure de refroidissement pour dispositif de palier Download PDF

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Publication number
WO2019188621A1
WO2019188621A1 PCT/JP2019/011602 JP2019011602W WO2019188621A1 WO 2019188621 A1 WO2019188621 A1 WO 2019188621A1 JP 2019011602 W JP2019011602 W JP 2019011602W WO 2019188621 A1 WO2019188621 A1 WO 2019188621A1
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WO
WIPO (PCT)
Prior art keywords
outer ring
spacer
ring spacer
inner ring
bearing
Prior art date
Application number
PCT/JP2019/011602
Other languages
English (en)
Japanese (ja)
Inventor
惠介 那須
岡本　直也
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 JP2018064299A external-priority patent/JP7164962B2/ja
Priority claimed from JP2018064231A external-priority patent/JP6946224B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2019188621A1 publication Critical patent/WO2019188621A1/fr

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Classifications

    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/08—Rigid support of bearing units; Housings, e.g. caps, covers for spindles
    • 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
    • F16C37/00—Cooling of bearings

Definitions

  • the present invention relates to a cooling structure for a bearing device, for example, a main shaft of a machine tool and a cooling structure for a bearing device incorporated in the main shaft.
  • Patent Document 1 lubricates a bearing with grease, and discharges compressed air from an air supply port provided in an outer ring spacer toward an inner ring spacer so that the inner ring spacer and a bearing adjacent thereto are discharged. Cool the spindle and so on.
  • Some spindle devices of machine tools have an air purge function using compressed air in order to prevent cleaning fluid, cutting fluid, chips generated during machining from entering inside (for example, Patent Document 2).
  • the compressed air supplied from the outside to the inside of the housing is discharged to the outside through a path that bypasses the bearing, so that impurities contained in the compressed air are contained in the bearing. It prevents adhesion and leakage of grease applied to the bearing.
  • the compressed air A2 for air purge passes through the air purge path 43 provided in the front lid 14 of the housing 2 and flows into the gap 44 between the main shaft 1 and the front lid 14, and from this gap 44 to the main shaft 1. It is discharged to the outer periphery of the tip of the.
  • the object of the present invention is to effectively use the compressed air, so that both the cooling of the rolling bearing and the air purge can be effectively performed while suppressing the amount of the compressed air used, and the housing is not greatly processed. It is an object to provide a cooling structure for a bearing device that can be configured.
  • Another object of the present invention is to effectively use the compressed air, so that both the cooling of the rolling bearing and the air purge can be effectively performed while suppressing the amount of the compressed air used, and no special rolling bearing is used. It is providing the cooling structure of the bearing apparatus which can be comprised in this.
  • an outer ring spacer and an inner ring spacer are respectively disposed adjacent to an outer ring and an inner ring of a rolling bearing, the outer ring and the outer ring spacer are installed in a housing, and the inner ring and the inner ring
  • An air supply port for blowing cooling compressed air toward the outer peripheral surface of the inner ring spacer is provided on the inner peripheral surface of the outer ring spacer, and a spacer space between the inner ring spacer and the outer ring spacer
  • An exhaust path for guiding the compressed air to the outer periphery of the tip of the rotary shaft from The exhaust path is configured by a through hole provided through the outer ring in the axial direction, or configured to pass through the inside of the housing.
  • the exhaust path is constituted by a through hole provided through the outer ring in the axial direction
  • compressed air for cooling is directed toward the outer peripheral surface of the inner ring spacer from the air supply port provided in the outer ring spacer. And sprayed.
  • the compressed air that has collided with the inner ring spacer removes heat from the inner ring spacer, thereby efficiently cooling the inner ring and the rotating shaft of the adjacent rolling bearing.
  • the compressed air after cooling the rolling bearing or the like passes through the exhaust path and is discharged to the outer periphery of the tip of the rotating shaft, and blows away the cleaning liquid, cutting liquid, chips, and the like existing in the periphery.
  • the through hole may be provided in an outer ring located on a distal end side of the rotation shaft with respect to the outer ring spacer.
  • the spacer space and the outer periphery of the tip of the rotating shaft can be connected by the shortest distance by the through hole, and the exhaust path is simplified.
  • the cross-sectional area of the through-hole may become smaller toward the tip end side of the rotating shaft.
  • the flow rate of the compressed air blown to the outer periphery of the tip of the rotating shaft increases, and the air purge effect is enhanced.
  • the exhaust path When the exhaust path is passed through the housing, the exhaust path can be completed with the housing alone. Therefore, it is not necessary to use a special rolling bearing.
  • the exhaust path includes an in-housing path part provided inside the housing, and a communication path part that communicates the spacer space and the in-housing path part.
  • the groove may be provided in the axial end surface of the outer ring spacer.
  • the communication path portion may be provided on both axial end surfaces of the outer ring spacer.
  • the compressed air in the spacer space is exhausted from both axial ends of the outer ring spacer to the path portion in the housing, the flow of compressed air in the spacer space is less uneven and the inner ring spacer is evenly distributed. Can be cooled to.
  • the rolling bearing may be grease lubricated.
  • the amount of compressed air passing through the bearing space between the inner ring and the outer ring in the rolling bearing can be reduced. For this reason, when the rolling bearing is lubricated with grease, leakage of grease in the bearing space can be suppressed.
  • the compressed air supplied from the air supply port that protrudes to the outer diameter side at both axial ends of the inner ring spacer flows into the bearing space between the inner ring and the outer ring in the rolling bearing.
  • An obstacle wall that prevents this may be provided. Since the obstacle wall prevents the compressed air from flowing into the bearing space, the leakage of grease in the bearing space can be further suppressed.
  • the air supply port is provided so as to be inclined forward in the rotational direction of the rotary shaft, and from an arbitrary radial straight line in a cross section perpendicular to the axis of the outer ring spacer, a direction orthogonal to the straight line
  • the position may be offset to
  • the air supply port is inclined as described above, the compressed air blown out from the air supply port flows in the axial direction while turning along the outer peripheral surface of the inner ring spacer.
  • the time during which the compressed air is in contact with the outer peripheral surface of the inner ring spacer becomes longer than when the compressed air flows straight in the axial direction, and the inner ring spacer can be cooled more efficiently.
  • FIG. 9 is a transverse sectional view taken along line VV in FIG. 8. It is a transverse cross section of a bearing device provided with a cooling structure concerning a 4th embodiment. It is sectional drawing of the conventional bearing apparatus.
  • FIG. 1 is a sectional view showing the entire bearing device.
  • This bearing device is for a machine tool, and a tool or a chuck is attached to the distal end side (left side in the figure) of a main shaft 1 that is a rotating shaft.
  • the main shaft 1 is rotatably supported with respect to the housing 2 by rolling bearings 3, 4, and 5 at the front end portion and the rear end portion separated in the axial direction.
  • the rolling bearings 3 and 4 that support the front end portion of the main shaft 1 are both angular ball bearings, and are arranged in combination on the back surface. Another rolling bearing that supports the tip portion of the main shaft 1 may be provided at a position closer to the rear end side than these rolling bearings 3 and 4.
  • the rolling bearing 5 that supports the rear end portion of the main shaft 1 is a cylindrical roller bearing and is used alone. A plurality of these bearings may be used.
  • the bearing device for the main shaft is a so-called built-in motor drive system in which a motor is built in the housing 2, and the built-in motor is interposed between the rolling bearings 3 and 4 on the front end side and the rolling bearing 5 on the rear end side. 7 is provided.
  • the built-in motor 7 includes a rotor 8 attached to the main shaft 1 and a stator 9 attached to the housing 2.
  • the rotor 8 is made of a permanent magnet or the like.
  • the stator 9 includes a coil and a core.
  • the housing 2 has a housing main body 11 and a rear housing member 12 disposed on the rear end side of the housing main body 11.
  • the housing 2 has a cylindrical motor housing member 13 fitted to the inner periphery of the housing main body 11 at substantially the same axial position as the built-in motor 7.
  • the housing 2 further includes a front lid 14 provided in contact with the distal end surface of the housing body 11.
  • the outer rings 3 a and 4 a of the rolling bearings 3 and 4 are fitted on the inner periphery of the front end portion of the housing body 11.
  • An outer ring 5 a of the rolling bearing 5 is fitted on the inner periphery of the rear housing member 12.
  • Inner rings 3 b, 4 b, 5 b of the rolling bearings 3, 4, 5 are respectively fitted on the outer peripheral surface of the main shaft 1.
  • the stator 9 is attached to the inner periphery of the motor housing member 13.
  • FIG. 2 shows a main part of a bearing device to which the cooling structure of the present invention is applied.
  • FIGS. 3 and 4 are diagrams showing different portions of FIG.
  • the rolling bearings 3 and 4 that support the tip portion of the main shaft 1 are angular ball bearings as described above, and a plurality of rolling elements 3c and 4c are interposed between the raceways of the outer rings 3a and 4a and the inner rings 3b and 4b. These rolling elements 3c and 4c are held equally in the circumferential direction by the cages 3d and 4d.
  • the pair of rolling bearings 3 and 4 are installed in a rear combination arrangement, but may be a front combination arrangement.
  • seal members 3e and 3f are respectively attached to both ends of the outer ring 3a in the axial direction.
  • Each of the seal members 3e and 3f is attached by fitting an outer diameter end into a circumferential groove provided in the outer ring 3a, and a seal lip at the inner diameter end is in contact with or close to the outer peripheral surface of the inner ring 3b.
  • Grease is sealed in a bearing space surrounded by the outer ring 3a, the inner ring 3b, and the seal members 3e and 3f on both sides.
  • the rolling bearing 4 also has seal members 4e and 4f attached to both ends in the axial direction of the outer ring 4a.
  • Each of the seal members 4e and 4f is attached by fitting an outer diameter end into a circumferential groove provided in the outer ring 4a, and a seal lip at the inner diameter end is in contact with or close to the outer peripheral surface of the inner ring 4b.
  • Grease is sealed in a bearing space surrounded by the outer ring 4a, the inner ring 4b, and the seal members 4e and 4f on both sides.
  • an outer ring spacer 15 and an inner ring spacer 16 are interposed between the pair of rolling bearings 3 and 4, respectively.
  • the outer ring spacer 15 is fitted to the inner periphery of the housing body 11, and the inner ring spacer 16 is fitted to the main shaft 1.
  • the outer ring 3 a of the rolling bearing 3 is positioned in the axial direction by the outer ring spacer 15 and the front lid 14.
  • the outer ring 4 a of the rolling bearing 4 is positioned in the axial direction by the outer ring spacer 15 and the step surface 11 of the housing body 11.
  • the inner ring 3 b of the rolling bearing 3 is positioned in the axial direction by an inner ring spacer 16 and a front positioning spacer 17.
  • the front positioning spacer 17 is a rotating body arranged on the rear end side of the front end flange portion 1 a of the main shaft 1.
  • the inner ring 4 b of the rolling bearing 4 is positioned in the axial direction by an inner ring spacer 16 and a rear positioning spacer 18.
  • the outer ring spacer 15 has a convex cross section including a cylindrical portion 15 a and an annular convex portion 15 b that protrudes from the axial center of the cylindrical portion 15 a toward the inner diameter side.
  • the inner ring spacer 16 has a concave cross section composed of a cylindrical portion 16a and a pair of obstacle walls 16b projecting from both axial ends of the cylindrical portion 16a to the outer diameter side.
  • the inner peripheral surface of the annular convex portion 15 b of the outer ring spacer 15 and the outer peripheral surface of the cylindrical portion 16 a of the inner ring spacer 16 are opposed to each other with a radial gap 20 therebetween.
  • the inner ring spacer 16 On both sides in the axial direction of the annular protrusion 15b, there are spacer spaces 21A and 21B where the outer ring spacer 15 and the inner ring spacer 16 face each other with a certain distance.
  • the inner ring spacer 16 is divided into two at an axial intermediate portion, for example. .
  • the obstacle wall 16b of the inner ring spacer 16 has a shape that protrudes toward the outer diameter side as it goes outward in the axial direction, and the outer diameter end of the outer ring of the rolling bearings 3 and 4 in both the circumferential direction and the axial direction. It is close to 3a and 4a.
  • an axial gap 22 having a labyrinth effect is formed between the axially outer side surface of the obstacle wall 16b and the seal members 3e and 4e.
  • An air supply port 23 for blowing compressed air A for cooling toward the outer peripheral surface of the cylindrical portion 16 a of the inner ring spacer 16 is provided on the inner peripheral surface of the annular convex portion 15 b of the outer ring spacer 15.
  • the number of air supply ports 23 is three, and the air supply ports 23 are equally arranged in the circumferential direction.
  • the compressed air A is supplied from an air compressor (not shown) provided outside the bearing device. That is, as shown in FIG. 1, an air intake port 24 connected to the air compressor is opened on the outer peripheral surface of the housing body 11, and an air supply path 25 following the air intake port 24 is formed inside the housing body 11. Has been.
  • the air supply path 25 extends to the outer peripheral surface of the outer ring spacer 15.
  • an introduction groove 26 for introducing the compressed air A is provided on the outer peripheral surface of the outer ring spacer 15.
  • the introduction groove 26 is provided in the middle in the axial direction on the outer peripheral surface of the outer ring spacer 15, and communicates with each air supply port 23 through the same number of connection holes 27 as the air supply ports 23.
  • the connection hole 27 is a hole extending in the radial direction, for example.
  • the air supply port 23 is a nozzle-like hole having a hole diameter smaller than that of the connection hole 27.
  • an exhaust path 30 that guides the compressed air A from the spacer spaces 21 ⁇ / b> A and 21 ⁇ / b> B to the external space on the tip end side of the main shaft 1 is configured.
  • the exhaust passage 30 includes a spacer through hole 31, an outer ring through hole 32, and an exhaust gap 33.
  • the spacer through hole 31 is provided so as to penetrate in the axial direction from the base portion of the annular convex portion 15b of the outer ring spacer 15 to the cylindrical portion 15a, and communicates the spacer spaces 21A and 21B on both sides.
  • the spacer through hole 31 is a tapered circular hole whose cross-sectional area decreases as it goes to the tip side of the main shaft 1. As shown in FIG. 5, in this example, the number of spacer through holes 31 is three, and each spacer through hole 31 is arranged between adjacent air supply ports 23.
  • the outer ring through-hole 32 shown in FIG. 4 is provided so as to penetrate the outer ring 3a of the rolling bearing 3 on the distal end side in the axial direction, and communicates the spacer space 21A on the distal end side with the exhaust gap 33.
  • the outer ring through hole 32 is also a tapered circular hole whose cross-sectional area becomes smaller toward the tip side.
  • the number of outer ring through-holes 32 is the same as that of the spacer through-holes 31, and the axis centers of the spacer through-holes 31 and the outer ring through-holes 32 coincide.
  • the spacer space 21A and the exhaust gap 33 can be connected with the shortest distance, and the exhaust path 30 is formed. Simple configuration.
  • the exhaust gap 33 is an annular gap formed between the front lid 14, the main shaft 1 and the positioning spacer 17 on the front side, and has a labyrinth structure whose cross-sectional shape is bent in a complicated manner. For this reason, it is possible for the compressed air A to flow through the exhaust gap 33 from the outer ring through-hole 32 to the outer space on the tip side of the main shaft 1, but when the compressed air A is not flowing, foreign matter passes in the opposite direction. It is suppressed.
  • the compressed air A is discharged from the spacer spaces 21A and 21B to the external space on the front end side of the main shaft 1 through the exhaust passage 30 of FIG. Thereby, the air purge action which blows away the cleaning fluid, cutting fluid, chips, etc. existing on the outer periphery of the tip flange portion 1a of the main shaft 1 is obtained. Since the cross-sectional area of the spacer through hole 31 of the exhaust passage 30 decreases toward the front end side of the main shaft 1, the compressed air A flows from the rear end side spacer space 21 ⁇ / b> B to the front end side spacer space 21 ⁇ / b> A of the main shaft 1. Flows smoothly.
  • the cross-sectional area of the outer ring through hole 32 decreases toward the tip end side of the main shaft 1, the flow rate of the compressed air A increases in the process of passing through the outer ring through hole 32. For this reason, the speed of the compressed air A blown from the exhaust gap 33 to the external space is increased, and an effective air purge can be performed.
  • the amount of compressed air A passing through the bearing space of the rolling bearings 3 and 4 can be reduced by exhausting the compressed air A from the spacer spaces 21A and 21B through the exhaust path 30. For this reason, leakage of grease in the bearing space can be suppressed.
  • the obstacle walls 16b are provided at both axial ends of the inner ring spacer 16, so that the compressed air A is prevented from flowing into the bearing space, and grease leaks in the bearing space. Can be further suppressed.
  • the compressed air A used for cooling the inner ring spacer 16 and the rolling bearings 3 and 4 is also used for air purge, the amount of compressed air A used can be reduced. Therefore, even with a relatively small capacity air compressor, both cooling and air purging of the inner ring spacer 16 and the rolling bearings 3 and 4 can be effectively performed.
  • the housing 2 Since the exhaust passage 30 is constituted by the spacer through hole 31 and the outer ring through hole 32 provided in the inner ring spacer 16 and the outer ring 3a of the rolling bearing 3, respectively, the housing 2 may be provided with no or a minimum exhaust path. It is only necessary to provide an exhaust path. For this reason, an air purge function can be added to the air-cooled main shaft device without subjecting the housing 2 to large processing.
  • connection hole 27 and the air supply port 23 are inclined so that the inner diameter side is located in front of the rotation direction of the main shaft 1 (indicated by a rotation arrow). Also good.
  • the connection hole 27 and the air supply port 23 are offset from an arbitrary radial straight line L in a cross section perpendicular to the axial center of the outer ring spacer 15 at a constant interval D in a direction perpendicular to the straight line L. is there.
  • connection hole 27 and the air supply port 23 are inclined as described above, the compressed air A blown from the air supply port 23 flows in the axial direction while turning along the outer peripheral surface of the inner ring spacer 16.
  • the compressed air A turns, the time during which the compressed air A is in contact with the outer peripheral surface of the inner ring spacer 16 becomes longer than when the compressed air A flows straight in the axial direction, and the inner ring spacer 16 can be cooled more efficiently. it can. Therefore, the cooling effect is improved and the amount of compressed air A used can be suppressed.
  • connection hole 27 and the air supply port 23 are inclined, when the compressed air A blown out from the air supply port 23 hits the outer peripheral surface of the inner ring spacer 16, the pressing force of the compressed air A is changed to the inner ring spacer. 16 and can be expected to drive the main shaft 1.
  • the rolling bearings 3 and 4 are of a grease lubrication system, but the cooling structure of the present invention can also be applied when the rolling bearings 3 and 4 are of an oil lubrication system such as air oil or oil mist. .
  • FIG. 7 is a sectional view showing the entire bearing device.
  • FIG. 8 shows a main part of a bearing device to which the cooling structure of the present invention is applied.
  • FIG. 9 is a view showing a part of FIG.
  • the same reference numerals are given and description thereof is omitted.
  • An air supply port 23 for blowing compressed air A for cooling toward the outer peripheral surface of the cylindrical portion 16 a of the inner ring spacer 16 is provided on the inner peripheral surface of the annular convex portion 15 b of the outer ring spacer 15.
  • the number of air supply ports 23 is three, and each air supply port 23 is equally distributed in the circumferential direction. It is said that.
  • the compressed air A is supplied from an air compressor (not shown) provided outside the bearing device. That is, as shown in FIG. 7, an air intake port 24 connected to the air compressor is opened on the outer peripheral surface of the housing body 11, and an air supply path 25 following the air intake port 24 is formed inside the housing body 11. Has been.
  • the air supply path 25 extends to the outer peripheral surface of the outer ring spacer 15.
  • an introduction groove 26 for introducing the compressed air A is provided on the outer peripheral surface of the outer ring spacer 15.
  • the introduction groove 26 is provided in the middle in the axial direction on the outer peripheral surface of the outer ring spacer 15, and communicates with each air supply port 23 through the same number of connection holes 27 as the air supply ports 23.
  • the connection hole 27 is a hole extending in the radial direction, for example.
  • the air supply port 23 is a nozzle-like hole having a hole diameter smaller than that of the connection hole 27.
  • Compressed air A taken in from the air intake port 24 (FIG. 7) passes through the air supply path 25, the introduction groove 26, and the connection hole 27 in this order, and from the air supply port 23 to the outer periphery of the cylindrical portion 16a of the inner ring spacer 16 Sprayed toward the surface.
  • an exhaust path 300 is configured to guide the compressed air A from the spacer spaces 21 ⁇ / b> A and 21 ⁇ / b> B to the external space on the tip end side of the main shaft 1.
  • the exhaust path 300 includes a connecting path portion 301 provided in the outer ring spacer 15 and an in-housing path portion 302 provided inside the housing 2.
  • the number of the exhaust paths 300 is not particularly limited, but is provided, for example, at three locations in the circumferential direction.
  • the communication path portion 301 is a radial groove provided on both axial end surfaces of the cylindrical portion 15 a of the outer ring spacer 15.
  • the communication path portion 301 formed of this groove has a rectangular cross section as shown in FIG. 10A, for example, and the outer rings 3a and 4a of the rolling bearings 3 and 4 in FIG. It becomes a hole shape.
  • the circumferential position of the communication path portion 31 may be the same as that of the air supply port 23 as shown in FIG. 10A or may be shifted from the air supply port 23 as shown in FIG. 10B.
  • the in-housing path portion 302 is connected to two radial direction portions 302 a extending to the outer diameter side inside the housing main body 11 following the communication path portion 301, and the outer diameter ends of these radial direction portions 302 a.
  • 11 includes an axial portion 302b that extends in the axial direction, and a bent portion 302c that is formed inside the front lid 14 and connects the front end of the axial portion 302b and the exhaust gap 303.
  • the exhaust gap 303 is an annular gap formed between the front lid 14, the main shaft 1, and the front positioning spacer 17, and the bent portion 302 c is formed in a gap portion between the front lid 14 and the main shaft 1.
  • the tip of is open.
  • the rear end of the exhaust gap 303 is connected to the bearing space of the front rolling bearing 3. For this reason, when the pressure in the bearing space is high, the air in the bearing space flows through the exhaust gap 303 to the external space on the tip side of the main shaft 1.
  • the cross-sectional shape of the exhaust gap 303 has a labyrinth structure that is bent in a complicated manner as a whole, it is possible to prevent foreign matter from passing from the external space on the tip end side of the main shaft 1 to the bearing space.
  • cooling air A is blown from the air supply port 23 provided in the outer ring spacer 15 toward the outer peripheral surface of the cylindrical portion 16 a of the inner ring spacer 16 during operation.
  • the compressed air A flows through the radial gap 20 into the spacer spaces 21A and 21B on both axial sides. During this time, the compressed air A removes heat from the inner ring spacer 16 to efficiently cool the inner rings 3b, 4b and the main shaft 1 of the rolling bearings 3, 4 adjacent thereto.
  • the compressed air A in the spacer spaces 21 ⁇ / b> A and 21 ⁇ / b> B passes through the exhaust path 300 and is discharged from the exhaust gap 33 to the external space on the tip side of the main shaft 1. Thereby, the air purge action which blows away the cleaning fluid, cutting fluid, chips, etc. existing on the outer periphery of the tip flange portion 1a of the main shaft 1 is obtained.
  • the amount of compressed air A passing through the bearing space of the rolling bearings 3 and 4 can be reduced by exhausting the compressed air A from the spacer spaces 21A and 21B through the exhaust path 300. For this reason, leakage of grease in the bearing space can be suppressed.
  • the obstacle walls 16b are provided at both axial ends of the inner ring spacer 16, so that the compressed air A is prevented from flowing into the bearing space, and grease leaks in the bearing space. Can be further suppressed.
  • the compressed air A used for cooling the inner ring spacer 16 and the rolling bearings 3 and 4 is also used for air purge, the amount of compressed air A used can be reduced. Therefore, even with a relatively small capacity air compressor, both cooling and air purging of the inner ring spacer 16 and the rolling bearings 3 and 4 can be effectively performed.
  • the exhaust path 300 By passing the exhaust path 300 through the inside of the housing 2, the exhaust path 300 can be completed only by the housing 2. Therefore, it is not necessary to use special rolling bearings 3 and 4.
  • connection hole 27 and the air supply port 23 are inclined so that the inner diameter side is located in front of the rotation direction of the main shaft 1 (indicated by a rotation arrow). You may let them.
  • the connection hole 27 and the air supply port 23 are offset from an arbitrary radial straight line L in a cross section perpendicular to the axial center of the outer ring spacer 15 at a constant interval D in a direction perpendicular to the straight line L. is there.
  • the rolling bearings 3 and 4 are of a grease lubrication system, but the cooling structure of the present invention is also applied when the rolling bearings 3 and 4 are of an oil lubrication system such as air oil or oil mist. Can do.
  • the machine tool since the air purge and cooling of the bearing device can be performed with a common compressed air, the machine tool can be reduced in size and energy consumption can be suppressed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

La présente invention concerne un dispositif de palier comportant une entretoise de bague externe (15) et une entretoise de bague interne (16) qui sont intercalées de manière à être respectivement adjacentes aux bagues externes (3a, 4a) et aux bagues internes (3b, 4b) de paliers à roulement (3, 4). Les bagues externes (3a, 4a) et l'entretoise de bague externe (15) sont installées dans un logement (2), et les bagues internes (3b, 4b) et l'entretoise de bague interne (16) sont installées dans un arbre rotatif (1). Un orifice d'alimentation en air (23), qui souffle de l'air comprimé de refroidissement (A) vers la surface circonférentielle externe de l'entretoise de bague interne (16), est placé dans la surface circonférentielle interne de l'entretoise de bague externe (15). Un passage d'évacuation, qui guide l'air comprimé (A) à partir d'espaces d'entretoise (21A, 21B) jusqu'à la circonférence externe de la pointe de l'arbre rotatif (1), est conçu en tant que passage d'évacuation (30) constitué de trous traversants (31) prévus pour pénétrer axialement dans la bague externe (3a), et en tant que passage d'évacuation (300) constitué de manière à passer à travers l'intérieur du logement (2).
PCT/JP2019/011602 2018-03-29 2019-03-19 Structure de refroidissement pour dispositif de palier WO2019188621A1 (fr)

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JP2018064299A JP7164962B2 (ja) 2018-03-29 2018-03-29 軸受装置の冷却構造
JP2018-064231 2018-03-29
JP2018064231A JP6946224B2 (ja) 2018-03-29 2018-03-29 軸受装置の冷却構造
JP2018-064299 2018-03-29

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TWI725883B (zh) * 2020-06-29 2021-04-21 肯岳亞股份有限公司 具流體迴路換模設備及換模設備之穩溫及除塵方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0645118U (ja) * 1992-11-27 1994-06-14 エヌティエヌ株式会社 軸受の潤滑装置
JP2011231885A (ja) * 2010-04-28 2011-11-17 Jtekt Corp 転がり軸受装置
WO2015072383A1 (fr) * 2013-11-18 2015-05-21 Ntn株式会社 Structure de refroidissement pour dispositif de palier

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Publication number Priority date Publication date Assignee Title
JP6560029B2 (ja) * 2015-06-09 2019-08-14 Ntn株式会社 モータ内蔵スピンドル用玉軸受

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0645118U (ja) * 1992-11-27 1994-06-14 エヌティエヌ株式会社 軸受の潤滑装置
JP2011231885A (ja) * 2010-04-28 2011-11-17 Jtekt Corp 転がり軸受装置
WO2015072383A1 (fr) * 2013-11-18 2015-05-21 Ntn株式会社 Structure de refroidissement pour dispositif de palier

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