WO2018074375A1 - Structure de refroidissement destinée à un dispositif palier - Google Patents

Structure de refroidissement destinée à un dispositif palier Download PDF

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Publication number
WO2018074375A1
WO2018074375A1 PCT/JP2017/037246 JP2017037246W WO2018074375A1 WO 2018074375 A1 WO2018074375 A1 WO 2018074375A1 JP 2017037246 W JP2017037246 W JP 2017037246W WO 2018074375 A1 WO2018074375 A1 WO 2018074375A1
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WO
WIPO (PCT)
Prior art keywords
ring spacer
outer ring
cooling structure
lubricating fluid
peripheral surface
Prior art date
Application number
PCT/JP2017/037246
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English (en)
Japanese (ja)
Inventor
惠介 那須
真人 吉野
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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
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018074375A1 publication Critical patent/WO2018074375A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
    • B23Q11/12—Arrangements for cooling or lubricating parts of the machine
    • 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
    • F16C19/18—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 two or more rows 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
    • 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
    • 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 incorporated in the main shaft.
  • an annular recess is provided on the peripheral surface of the outer ring spacer facing the inner ring spacer, an outlet is provided in the recess, an air nozzle is provided, and cooling air is directed toward the peripheral surface of the inner ring spacer.
  • a cooling structure for discharging is proposed (Patent Document 2).
  • the outer ring spacer is provided with lubricating fluid discharge means for supplying lubricating air oil to the rolling bearings on both sides. According to this configuration, the compressed air is adiabatically expanded by being discharged at a stroke from the narrow nozzle hole into the space formed by the recess. As a result, the flow rate of compressed air increases and the temperature decreases. Therefore, the rotating side spacer is efficiently cooled.
  • JP 2000-161375 A Japanese Patent Laying-Open No. 2015-183738
  • the cooling structure of the bearing device of Patent Document 2 provides an excellent cooling function.
  • the configuration is such that two rows of rolling bearings are similarly cooled, and in the arrangement of bearings arranged in three or more rows, the cooling function for each rolling bearing cannot be individually adjusted.
  • the temperature rise of the rolling bearing differs depending on the drive system and the bearing arrangement. Therefore, in order to use limited compressed air efficiently, the bearing temperature is high (the temperature of the inner ring and the outer ring). It is necessary to intensively cool the areas where the difference is large.
  • the cooling structure of the bearing device of Patent Document 2 it is possible to apply the cooling structure of the bearing device of Patent Document 2 to two adjacent rolling bearings. In that case, the temperature of each two rolling bearings Therefore, it is difficult to adjust the cooling function according to the arrangement location of the rolling bearings.
  • the object of the present invention is that it is possible to adjust the cooling function according to the arrangement location of the rolling bearings for the rolling bearings arranged in three or more rows, and the rolling bearing which is the main cooling purpose can be efficiently cooled, It is another object of the present invention to provide a cooling structure for a bearing device that can alleviate a mixed flow of a lubricating fluid and compressed air.
  • the cooling structure for a bearing device is a cooling structure for a bearing device in which an outer ring spacer and an inner ring spacer are interposed between outer rings and inner rings of adjacent rolling bearings in an arrangement of rolling bearings arranged in three or more rows in the axial direction.
  • Lubricating fluid discharge means for supplying a lubricating fluid containing air and lubricating oil to a rolling bearing on the corresponding side of the rolling bearing adjacent to the outer ring spacer is adjacent to the outer ring spacer.
  • a portion of the annular space on the supply side of the lubrication fluid (the side on which the lubrication fluid discharge means is provided) with respect to the central axis of the air nozzle is a non-supply side (the lubrication fluid discharge means is provided). It is characterized by having a larger volume than the part on the non-side.
  • the annular space between the outer ring spacer and the inner ring spacer has a larger volume on the supply side of the lubricating fluid than the non-supply side portion with respect to the central axis of the air nozzle. Since the compressed air discharged to the side tends to flow toward the space part having a large volume, the compressed air easily flows to the rolling bearing on the supply side of the lubricating fluid. Therefore, this rolling bearing can be effectively cooled. Further, since the amount of compressed air flowing into the opposite rolling bearing is reduced, the mixed flow of the lubricating fluid and the compressed air supplied from the other outer ring spacer in the opposite rolling bearing is alleviated.
  • the rolling bearing that is the main cooling purpose can be efficiently cooled.
  • the compressed air discharged from the narrow air nozzle is discharged at a stretch into a wide annular space, so that the compressed air is adiabatically expanded.
  • the flow rate of compressed air increases and the temperature decreases. Therefore, the inner ring spacer is efficiently cooled, the temperature of the compressed air flowing into the rolling bearing is low, and the rolling bearing is also efficiently cooled.
  • the lubricating fluid is, for example, air oil or oil mist.
  • the said annular space may be formed only by the said recessed part provided in the internal peripheral surface of the said outer ring
  • the annular space is formed only by the recessed portion of the outer ring spacer, the inner ring spacer has a simple shape, and the processing of the spacer is easy.
  • the said annular space may be formed by the said recessed part provided in the inner peripheral surface of the said outer ring spacer, and the said recessed part provided in the outer peripheral surface of the said inner ring spacer.
  • the recessed portion is formed in both the outer ring spacer and the inner ring spacer, a large volume of the annular space can be obtained, and the adiabatic expansion effect can be enhanced.
  • the axial length of the portion on the supply side of the lubricating fluid may be longer than the axial length of the portion on the non-supply side.
  • the annular space is difficult to vary in size in the radial direction due to limitations on the thickness of the inner ring spacer and outer ring spacer, but it is easy to change the size in the axial direction. .
  • the length of the gap between the outer ring spacer and the inner ring spacer in the axial direction is shortened on the large volume side, and the flow resistance is reduced. . Therefore, the compressed air is more likely to flow to the rolling bearing on the supply side of the lubricating fluid.
  • the lubricating fluid discharge means continues to the outer ring spacer provided for only one of the rolling bearings adjacent to the outer ring spacer on the side where the lubricating fluid discharge means is not provided.
  • An air nozzle that discharges compressed air to an annular space between the outer ring spacer and the corresponding inner ring spacer is provided in an outer ring spacer between two rolling bearings arranged in parallel, and the lubricating fluid discharge means is disposed between the outer rings. It may be provided for both rolling bearings adjacent to the seat.
  • one outer ring spacer has two fluid discharge means for lubrication to be supplied to the rolling bearings on both sides and to supply compressed air to the rolling bearings on both sides,
  • the number of outer ring spacers having the lubricating fluid discharge means and the air nozzle can be reduced. Cooling adjustment is performed in the same manner for both rolling bearings. However, only one of the rolling bearings described above has lubricating fluid discharge means, and compressed air is concentrated on one of the rolling bearings. Since it is combined with the outer ring spacer to be fed, the cooling function can be adjusted according to the arrangement location of the rolling bearings.
  • the annular space between the outer ring spacer and the inner ring spacer in which the lubricating fluid discharge means is provided for both rolling bearings adjacent to the outer ring spacer is the outer ring. It is good also as a structure formed by the cyclic
  • the outer ring spacer provided with the two fluid discharge means for lubrication also provides an increase in the flow rate of compressed air and a decrease in temperature due to the adiabatic expansion by providing the recess and expanding the annular space.
  • the lubricating fluid discharge means has a flange protruding so as to cover the outer peripheral surface of the inner ring in the rolling bearing on the side corresponding to the lubricating fluid discharge means, and an opening in the inner peripheral surface of the flange And a lubricating nozzle for discharging the lubricating fluid.
  • a cooling structure for a bearing device according to a first embodiment of the present invention will be described with reference to FIGS.
  • the cooling structure of the bearing device of this example is applied to a front-side bearing device in a spindle device of a machine tool. However, it is not limited only to the spindle device of the machine tool.
  • the bearing device J includes three or more rolling bearings 1 arranged in the axial direction, in the illustrated example, four rolling bearings 1, and between the outer rings 2 and 2 of the adjacent rolling bearings 1, 1 and the inner rings 3, 3.
  • An outer ring spacer 4 and an inner ring spacer 5 are interposed therebetween.
  • the subscript “I” is attached to the rolling bearings 1 in the center two rows
  • the subscript “O” is attached to the rolling bearings 1 at the end. ".
  • the outer ring 2 and the outer ring spacer 4 are installed in the housing 6, and the inner ring 3 and the inner ring spacer 5 are fitted to the main shaft 7.
  • the rolling bearing 1 is an angular ball bearing, and a plurality of rolling elements 8 are interposed between the raceways of the inner ring 3 and the outer ring 2. Each rolling element 8 is held at equal intervals in the circumferential direction by a cage 9.
  • the two center rolling bearings 1 I and 1 I are arranged in a rear combination, and each of the two rolling bearings 1 O and 1 O at both ends is arranged in the same direction as the adjacent rolling bearing 1 I.
  • the outer ring spacer 4 and the inner ring spacer 5 are provided with a difference in width, whereby the initial preload of each rolling bearing 1 is set and used.
  • the outer ring 2 and the outer ring spacer 4 are, for example, a clearance fit with respect to the housing 6, and are positioned in the axial direction by the step portion 6 a of the housing 6 and the end surface cover 40.
  • the inner ring 3 and the inner ring spacer 5 of the rolling bearing 1 are, for example, an interference fit with respect to the main shaft 7 and are positioned in the axial direction by the positioning spacers 41 and 42 on both sides. Note that the positioning spacer 42 on the left side of the figure is fixed by a nut 43 screwed onto the main shaft 7.
  • Each rolling bearing 1 is an inner ring rotation.
  • FIG. 2 shows a partially enlarged view between the rolling bearings 1 I and 1 I in the center two rows of FIG.
  • the outer ring spacer 4 includes an outer ring spacer main body 11 and ring-shaped flanges 12 and 12 made of different members from the outer ring spacer main body 11.
  • the flange 12 constitutes a lubricating fluid discharge means 30 described later.
  • the outer ring spacer main body 11 has a substantially T-shaped cross section, and the flanges 12 and 12 are fixed symmetrically on both sides of the outer ring spacer main body 11 in the axial direction.
  • the inner diameter dimension of the outer ring spacer main body 11 is larger than the inner diameter dimension of the flange portions 12 and 12.
  • the recessed part 13 comprised by the inner peripheral surface of the outer ring spacer main body 11 and the side surface of the collar parts 12 and 12 following this inner peripheral surface is formed in the inner peripheral surface of the outer ring spacer 4.
  • the recess 13 is an annular groove having a rectangular cross section.
  • An annular space 14 is formed between the outer ring 2 and the inner ring 3 by the recess 13.
  • the inner peripheral surface of the outer ring spacer 4 other than the recessed portion 13, that is, the inner peripheral surfaces of the flange portions 12 and 12, and the outer peripheral surface of the inner ring spacer 5 are opposed to each other via a minute radial clearance ⁇ a.
  • annular space 14 whose radial direction width is wider than others is formed.
  • the annular space 14 and the radial clearance ⁇ a on both sides thereof constitute a both-side exhaust path 58.
  • the outer ring spacer main body 11 is provided with an air nozzle 15 for discharging compressed air A for cooling toward the outer peripheral surface of the inner ring spacer 5.
  • the outlet 15 a of the air nozzle 15 opens in the recess 13 on the inner peripheral surface of the outer ring spacer 4.
  • a plurality of (for example, three) air nozzles 15 are arranged at equal intervals in the circumferential direction (see FIG. 3).
  • each air nozzle 15 is inclined forward in the rotational direction of the inner ring spacer 5. That is, the position is offset from an arbitrary radial straight line L in a cross section perpendicular to the axis of the outer ring spacer 4 in a direction orthogonal to the straight line L.
  • the reason for offsetting the air nozzle 15 is to improve the cooling effect by causing the compressed air A to act as a swirling flow in the rotation direction of the inner ring spacer 5.
  • the outer ring spacer 4 is indicated by a cross section passing through the center line of the air nozzle 15.
  • an introduction groove 16 for introducing the compressed air A into each air nozzle 15 from the outside of the bearing is formed in the outer peripheral surface of the outer ring spacer main body 11.
  • the introduction groove 16 is provided in an intermediate portion in the axial direction on the outer peripheral surface of the outer ring spacer 4 and is formed in an arc shape communicating with each air nozzle 15.
  • the introduction groove 16 is provided on the outer peripheral surface of the outer ring spacer main body 11 over an angular range ⁇ indicating most of the circumferential direction except a circumferential position where an air oil supply path (not shown) described later is provided. .
  • a compressed air introduction path 45 is provided in the housing 6, and the introduction groove 16 communicates with the compressed air introduction path 45.
  • An air supply device (not shown) for supplying the compressed air A to the compressed air introduction hole 45 is provided outside the housing 6.
  • FIG. 4 shows an enlarged view of the rolling bearing 1 O at the right end of FIG. 1 and the adjacent spacer.
  • the rolling bearing 1 O at the left end of FIG. 1 and the adjacent spacer are the same as those in FIG.
  • the rolling bearings 1 O at the end and the spacers adjacent thereto are the same as the rolling bearings 1 I and 1 I in the middle two rows and the spacers therebetween except for matters to be specifically described.
  • the outer ring spacer 4 of the end rolling bearing 1 O is provided only on one side where the flange portion 12 of the lubricating fluid supply means 30 is provided with the end rolling bearing 1 O serving as a main cooling purpose. Is provided.
  • the portion of the inner peripheral surface of the outer ring spacer 4 opposite to the flange portion 12 is a small diameter portion 2 a that is close to the outer peripheral surface of the inner ring spacer 5, similar to the flange portion 12.
  • An annular recess 13A is formed by the side surface of the small-diameter portion 2a, the side surface of the flange portion 12, and the inner peripheral surface of the central portion in the width direction of the outer ring spacer 4, and the recess 13A forms the annular ring recess 4A.
  • An annular space 14 ⁇ / b> A is formed between the inner peripheral surface and the outer peripheral surface of the inner ring spacer 5.
  • the side surface of the small diameter portion 2a on the annular space 14A side is an inclined surface in which the inner diameter side approaches the end portion in the spacer width direction.
  • the annular space 14A and the radial clearance ⁇ a on one side thereof constitute a one-side exhaust path 59.
  • Said annular space 14A is relative to the center axis O 15 of the air nozzle 15, the rolling bearing 1 O-side portion 14A1 of the end portion as a main purpose of the cooling, with larger volume than the portion 14A2 of the center of the rolling bearing 1 I side Thus, it is formed in an asymmetric shape in the axial direction. Specifically, the axial length of the portion 14A1 of the annular space 14A is longer than the axial length of the portion 14A2.
  • the ratio of the volume of both portions 14A1,14A2 of the annular space 14A for example 6: 4, 7: 3 and the like, are designed appropriately, the portion 14A2 of the smaller, distance from the center axis O 15 from the opening edge of the air nozzle 15
  • a range from the center axis O 15 to the rolling bearing 1 I in the direction to 1/5 of the outer ring spacer width is preferable, and more preferably the center axis O 15 to the rolling bearing 1 between the outer rings in the I side direction.
  • the range is up to 1/10 of the seat width.
  • each outer ring spacer 4 includes the flange portion 12 (FIGS. 2 and 4) as a means constituting a lubricating fluid discharge means 30.
  • Each flange 12 protrudes into the bearing and faces the outer peripheral surface of the inner ring 3 via an air oil passage annular clearance ⁇ b.
  • the flange portion 12 is disposed so as to enter the bearing so as to cover the outer peripheral surface of the inner ring 3. Further, the distal end portion of the flange portion 12 is disposed radially inward from the inner peripheral surface of the cage 9.
  • a lubrication nozzle 31 is provided for supplying, for example, air oil, which is opened to the annular clearance ⁇ b and serves as a lubrication fluid.
  • the lubricating nozzle 31 is inclined so as to reach the inner diameter side toward the bearing side, and an outlet is opened at an inner peripheral surface portion of the flange portion 12 facing the inner ring 3. Air oil is supplied to the lubricating nozzle 31 through a lubricating fluid supply path (not shown) provided in the housing 6 and the outer ring spacer body 11.
  • An annular recess 3 a is provided at a location on the extended line of the lubricating nozzle 31 on the outer peripheral surface of the inner ring 3.
  • the oil of the air oil discharged from the lubricating nozzle 31 of the collar portion 12 is accumulated in the annular recess 3a, and this oil is along the outer peripheral surface of the inner ring 3 which is an inclined surface by the centrifugal force accompanying the rotation of the inner ring 3. Guided to the bearing center side.
  • the bearing device J is provided with an exhaust path 46 for exhausting compressed air for cooling and air oil that is a lubricating fluid for lubrication.
  • the exhaust passage 46 includes an exhaust groove 47 provided in a part of the outer ring spacer body 11 in the circumferential direction, a radial exhaust hole 48 provided in the housing 6 and communicating with the exhaust groove 47, and an axial exhaust hole 49.
  • the exhaust groove 47 of the outer ring spacer body 11 is formed over a circumferential position diagonal to the position where the lubricating fluid supply path is provided.
  • the cooling structure of the bearing apparatus which consists of the said structure.
  • the cooling structure of this bearing device includes four rows of rolling bearings 2, and compressed air is branched and discharged from one air nozzle 15 for the two central rolling bearings 1 I and 1 I.
  • compressed air is individually discharged from the air nozzles 15 and 15. Therefore, the cooling function of each rolling bearing 1 can be adjusted according to the arrangement location of these rolling bearings 1. Moreover, about the cooling of each rolling bearing 1, it can cool efficiently as follows.
  • Compressed air A for cooling is blown toward the outer peripheral surface of the inner ring spacer 5 from the air nozzle 15 of each outer ring spacer 4 shown in FIGS.
  • the compressed air A is adiabatically expanded by being discharged from the narrow air nozzle 15 into the wide annular spaces 14 and 14A.
  • the volume of the compressed air in the air nozzle 15 is V1
  • the temperature is T1
  • the volume of the compressed air in the annular spaces 14, 14A is V2
  • the temperature is T2
  • the flow rate of the compressed air A increases.
  • the inner ring spacer 5 is efficiently cooled by blowing the compressed air A at a low temperature and high speed onto the inner ring spacer 5.
  • the compressed air A discharged from the air nozzle 15 flows in the axial direction while turning along the outer peripheral surface of the inner ring spacer 5. , And is discharged to the outside of the bearing through the exhaust passage 46. Since 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 5 is longer than when the straight air flows in the axial direction, and the inner ring spacer 5 can be cooled more efficiently. it can.
  • the inner ring spacer 5 is efficiently cooled, so that the inner ring 3 and the main shaft 7 of the rolling bearing 1 can be effectively cooled via the inner ring spacer 5. Since this cooling structure can improve cooling efficiency only by providing an annular recess 13, 13A on the inner peripheral surface of the outer ring spacer 4 and inclining the air nozzle 15, the cooling efficiency can be improved. It is not necessary to increase the output of the air supply device that supplies air A, and power consumption can be suppressed.
  • the compressed air A discharged into the annular spaces 14 and 14A between the recesses 13 and 13A and the inner ring spacer 5 passes through the radial clearance ⁇ a between the outer ring spacer 4 and the inner ring spacer 5 to the outside of the bearing. Is discharged. At that time, at least a part of the compressed air A flows into the bearing.
  • the flow velocity of each portion of the compressed air A flowing in the radial clearance ⁇ a in the circumferential direction is made uniform, and the flow velocity of the compressed air A flowing into the bearing is reduced. It becomes uniform. Thereby, the collision sound between the compressed air A and the rotating rolling element 9 can be reduced.
  • FIG. 5 the flow of compressed air is indicated by the outline line thickness arrow, and the flow of the lubricating fluid is indicated by the bold line arrow, and is discharged from the air nozzle 15 of the outer ring spacer 4 adjacent to the rolling bearing 1 O at the end.
  • compressed air passes through the gap between the outer ring spacer 4 and the inner ring spacer 5, enters the inner rolling bearing 1 I on the center side of the adjacent, to mixed flow to the flow of lubricating fluid.
  • the annular space 14A of the outer ring spacer 4 adjacent to the end rolling bearing 1 O is a portion of the end portion of the air nozzle 15 on the side of the rolling bearing 1 O with respect to the central axis O 15 .
  • 14A1 is, so that it has a greater volume than the portion 14A2 of the center of the rolling bearing 1 I side, are formed axially asymmetrical. That is, the annular space 14A is the center axis O 15 of the air nozzle 15, the portion 14A1 is non-supply side of the supply side of the lubricating fluid (lubricating side fluid discharge means is provided) (lubricating fluid delivery means It has a larger volume than the portion 14A2 on the side not provided.
  • the annular space 14B defined between the outer ring spacer 4 and the inner ring spacer 5 adjacent to the rolling bearing 1 O end is formed on the inner peripheral surface of the outer ring spacer 4 It is formed by a recess 13 a and the recess 13 b formed on the outer peripheral surface of the inner ring spacer 5.
  • the shape of the inner ring spacer 5 is a simple shape without unevenness. And it is easy to manufacture.
  • the annular space 14 ⁇ / b> B is formed by a recess 13 a formed in the outer ring spacer 4 and a recess 13 b formed in the inner ring spacer 5. If so, the volume of the annular space 14B can be increased, and the compressed air discharged from the air nozzle 15 can be sufficiently adiabatically expanded to enhance the cooling effect.
  • FIG. 8 is a cross-sectional view showing an outline of the entire spindle device of the machine tool to which each of the embodiments is applied.
  • the main shaft 7 has a front portion supported by the bearing device J according to any one of the above embodiments, and a rear portion supported by another rolling bearing 61.
  • An outer tube cooling type liquid cooling device 62 is provided on the outer periphery of the housing 6.
  • the rear end of the main shaft 7 is connected to an electric motor 63 outside the housing 6.
  • FIG. 9 shows another example of a spindle device of a machine tool to which the bearing device is applied, and is a built-in motor type.
  • An electric motor 63 ⁇ / b> A is provided between the front bearing device J and the rear bearing 61 in the housing 6.
  • the electric motor 63 ⁇ / b> A is a built-in motor including a stator 64 provided on the inner periphery of the housing 6 and a rotor 65 provided on the outer periphery of the main shaft 7.
  • the cooling structure of the bearing device of the present invention can be effectively applied to both the external motor type and the built-in motor type main shaft devices.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Turning (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

L'invention porte sur une structure de refroidissement destinée à un dispositif palier, un espace annulaire (14A) étant disposé entre une entretoise d'anneau externe (4) et une entretoise d'anneau interne (5), et l'entretoise d'anneau externe (4) étant munie d'une buse d'air (15) qui est ouverte vers l'espace annulaire (14A) et qui évacue de l'air comprimé. L'entretoise d'anneau externe (4) comporte, en son sein sur un seul côté d'une pluralité de paliers à rouleaux (1) adjacents à l'entretoise d'anneau externe (4), un moyen d'évacuation de fluide de lubrification (12) servant à fournir un fluide de lubrification tel que de l'huile-air au palier à rouleaux (1) sur le côté correspondant parmi les paliers à rouleaux (1) adjacents à l'entretoise d'anneau externe (4). L'espace annulaire (14A) a un volume supérieur dans une section (14A1) sur le côté où le fluide lubrifiant est fourni, que dans une section (14A2) du côté où le fluide de lubrification n'est pas fourni, par rapport à l'axe central (O15) de la buse d'air (15).
PCT/JP2017/037246 2016-10-17 2017-10-13 Structure de refroidissement destinée à un dispositif palier WO2018074375A1 (fr)

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JP2016203336A JP2018066384A (ja) 2016-10-17 2016-10-17 軸受装置の冷却構造
JP2016-203336 2016-10-17

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114850962A (zh) * 2022-06-09 2022-08-05 珠海格力电器股份有限公司 一种冷却***及电主轴

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JP2007303528A (ja) * 2006-05-10 2007-11-22 Jtekt Corp 転がり軸受
JP2008164080A (ja) * 2006-12-28 2008-07-17 Ntn Corp アンギュラ玉軸受装置
JP2014062617A (ja) * 2012-09-24 2014-04-10 Ntn Corp 軸受装置の冷却構造
JP2014062620A (ja) * 2012-09-24 2014-04-10 Ntn Corp 軸受装置の冷却構造
JP2015117820A (ja) * 2013-11-18 2015-06-25 Ntn株式会社 軸受装置の冷却構造
JP2016089975A (ja) * 2014-11-06 2016-05-23 Ntn株式会社 軸受装置の冷却構造

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007303528A (ja) * 2006-05-10 2007-11-22 Jtekt Corp 転がり軸受
JP2008164080A (ja) * 2006-12-28 2008-07-17 Ntn Corp アンギュラ玉軸受装置
JP2014062617A (ja) * 2012-09-24 2014-04-10 Ntn Corp 軸受装置の冷却構造
JP2014062620A (ja) * 2012-09-24 2014-04-10 Ntn Corp 軸受装置の冷却構造
JP2015117820A (ja) * 2013-11-18 2015-06-25 Ntn株式会社 軸受装置の冷却構造
JP2016089975A (ja) * 2014-11-06 2016-05-23 Ntn株式会社 軸受装置の冷却構造

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114850962A (zh) * 2022-06-09 2022-08-05 珠海格力电器股份有限公司 一种冷却***及电主轴

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