WO2017135073A1 - Ball bearing for spindle with built-in motor - Google Patents

Ball bearing for spindle with built-in motor Download PDF

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Publication number
WO2017135073A1
WO2017135073A1 PCT/JP2017/001926 JP2017001926W WO2017135073A1 WO 2017135073 A1 WO2017135073 A1 WO 2017135073A1 JP 2017001926 W JP2017001926 W JP 2017001926W WO 2017135073 A1 WO2017135073 A1 WO 2017135073A1
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Prior art keywords
spindle
mesh
ball bearing
bearing
outer ring
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PCT/JP2017/001926
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French (fr)
Japanese (ja)
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崇広 金本
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Ntn株式会社
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Publication of WO2017135073A1 publication Critical patent/WO2017135073A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F16J15/453—Labyrinth packings characterised by the use of particular materials

Definitions

  • the present invention relates to a ball bearing for a motor built-in spindle used in a small spindle, particularly a motor built-in spindle, and more particularly to a ball bearing provided with a seal member covering an end opening of a bearing space formed between an inner ring and an outer ring. It is.
  • Small spindle is mainly used for light load machining such as aluminum machining.
  • the spindle with a built-in motor has a motor 2 built in the housing 1 of the spindle, the periphery of the motor 2 becomes a main heat generation source, so the motor 2 needs to be cooled together with the bearing 3.
  • the cooling in the housing 1 of the spindle with a built-in motor is mainly performed with air that does not require a complicated structure.
  • the air that cools the inside of the spindle housing 1 cools the motor 2 and then the bearing 3 from the rear side by a vent hole 4 installed in the spindle housing 1, and the spindle housing 1 from the front end 1 a of the spindle 1 It is discharged outside the housing 1.
  • the tip of the spindle housing 1 also serves as a seal against flying objects, and the pressure inside the spindle housing 1 is increased by an air curtain and a labyrinth seal so that cutting fluid, work pieces, etc. are contained in the spindle housing 1. Preventing intrusion.
  • the bearing 3 used for the spindle with a built-in motor is filled with grease as a lubricant, and both end faces are sealed with seal plates.
  • Lubricant may leak to the outside. This leakage of the lubricant may affect the durability performance of the bearing.
  • the vibration of the cage is transmitted to the spindle housing 1 and adversely affects machining accuracy and quietness.
  • the present invention prevents leakage of lubricant to the outside of the bearing due to cooling air when cooling air enters the bearing of the spindle with a built-in motor, and suppresses turbulent flow of cooling air inside the bearing.
  • the purpose of the present invention is to provide a pindle ball bearing that suppresses the vibration of the cage and is highly quiet.
  • an inner ring and an outer ring a plurality of rolling elements interposed between the inner ring and the outer ring, a cage that holds the rolling elements, and an opening of a gap between the inner ring and the outer ring And a ball bearing for spindle formed by sealing a lubricant around the rolling element,
  • the seal member includes a gas-permeable mesh portion at least partially.
  • the mesh portion may be provided in a portion located on the inner diameter side of the inner diameter surface of the cage.
  • the seal member includes a mesh member constituting the mesh-like portion, and a support member provided on the mesh member so as to be attached to the outer ring, and the mesh member has an inner diameter side than the support member.
  • the projecting portion can be a mesh-shaped portion.
  • the mesh member can be composed of a nonwoven fabric of synthetic resin fibers.
  • the seal plate since at least a part of the seal plate is a mesh-like portion, a mesh-like portion that allows a gas such as cooling air to pass through while retaining the lubricant in the bearing. This allows the cooling air to pass outside the bearing. For this reason, stable sealing performance and permeability of the cooling air in the bearing can be ensured, respectively, and the lubricant can be leaked to the outside or the cage vibration due to the turbulent flow of the cooling air can be prevented. Therefore, both bearing life and acoustic performance can be achieved.
  • the ball bearing for spindle with a built-in motor is an angular ball bearing.
  • An angular ball bearing 10 includes an inner ring 11, an outer ring 12, rolling elements 13 disposed on the rolling surfaces facing the inner ring 11 and the outer ring 12, a cage 14 that holds the rolling elements 13,
  • a seal plate 15 is provided on both end faces of the inner ring 11 and the outer ring 12 and covers an opening of a gap between the inner and outer rings.
  • the space between the inner ring 11 and the outer ring 12 is filled with grease as a lubricant, and leakage to the outside is prevented by the seal plate 15.
  • a lubricant is stably supplied between the raceway of the outer ring 12 and the rolling element 13, and between the raceway of the outer ring 12 and the cage 14.
  • a grease pocket 20 is provided.
  • the grease which is a lubricant, is preferably enclosed by about 40% to 50% of the static space volume. In the case of 40% or less, it is difficult to obtain a stable durability effect due to the bias of grease due to air pressure. In the case of 50% or more, due to grease bias due to air pressure, excessive rewinding of grease leads to large temperature fluctuations and vibration fluctuations, and stable rotation cannot be obtained.
  • the base oil viscosity of the grease is preferably 20 to 40 mm 2 / s.
  • the inner ring surface of the outer ring 12 is provided with mounting grooves 16 at both ends in the axial direction, and the outer peripheral portion of the seal plate 15 is supported by the mounting grooves 16.
  • the seal plate 15 has its inner peripheral portion opposed to the outer peripheral surface 11a of the inner ring 11 with a small radial gap.
  • the outer diameter surface 11a of the inner ring 11 facing the inner diameter portion of the seal plate 15 is formed in a straight line as shown in FIGS.
  • a seal groove for forming a labyrinth structure is not formed between the radial surface and the radial surface.
  • the seal plate 15 has a configuration in which two types of plate members, a mesh member 17 and a support member 18, are laminated.
  • the seal plate 15 is in a state where the mesh member 17 and the support member 18 are laminated, and is manufactured by insert molding as an example.
  • the mesh member 17 located on the inner side in the axial direction of the seal plate 15 has a mesh structure having a gas permeability by forming synthetic resin fibers into a sheet shape by means of knitting or weaving. It is a member.
  • a synthetic resin fiber non-woven fabric filter is used.
  • the mesh member 17 is preferably configured to have a pressure loss of about 50%, and is configured to allow only cooling air to pass through.
  • the synthetic resin constituting the mesh member is preferably compatible with grease and does not chemically attack the grease, or has a volume change rate of 10% or less.
  • a support member 18 is provided outside the seal plate 15 in the axial direction.
  • the support member 18 is made of rubber or synthetic resin in consideration of the mounting property to the outer ring, and supports the mesh member 17 having flexibility.
  • the support member 18 is provided to support the mesh member 17 and to be attached to the outer ring, and the configuration thereof is not limited as long as these can be embodied.
  • the support member 18 can also be provided with a through hole or the like through which air can permeate at a location where the mesh member 17 is laminated and supported.
  • the mesh member 17 is provided in a state of projecting to the inner ring side from the support member 18, and the projecting portion is a mesh-shaped portion 15a. Since only the mesh member 17 that is an air permeable material is disposed in the mesh-like portion 15a, the cooling air can be passed therethrough.
  • the mesh-like portion 15 a in which the mesh member 17 protrudes to the inner ring side from the support member 18 is located on the inner diameter side from the inner diameter surface 14 a of the cage 14.
  • the cooling air can pass without receiving the resistance of the cage 14 from the inlet side to the outlet side of the passing air.
  • the outer peripheral surface 11a of the inner ring 11 is also provided linearly, the projected area of the gap between the outer diameter surface of the inner ring 11 on the outlet side and the mesh-like portion 15a of the seal plate 15 is increased. This is almost the same as the projected projection area of the air flow path passing through the bearing.
  • the seal plate has a projected area through which air can pass substantially linearly without resistance between the mesh-like portion 15a of the seal plate 15 and the outer diameter surface of the inner ring 11 facing the seal plate 15.
  • the outer diameter surface 11a of the inner ring 11 facing the inner diameter portion of the seal plate 15 is formed in a straight line.
  • a seal groove 19 that forms a labyrinth structure may be provided between the outer diameter surface of 11 and the sealability of grease can be improved.
  • both the bearing life and the acoustic performance can be achieved in order to prevent the passage of the cooling air while holding the lubricant inside the bearing.
  • the present invention is not limited to angular contact ball bearings, but can be applied to other types of ball bearings or combination ball bearings having a seal plate.
  • a rubber or resin support member is laminated on the mesh member.
  • the seal plate is partially or entirely mesh-shaped. As long as the mesh-shaped part has gas permeability.
  • the whole can be configured by a mesh member.
  • a support framework for reinforcing the mesh member may be embedded in the mesh member.

Abstract

The present invention addresses the problem of providing a quiet ball bearing for a spindle with a built-in motor that, when cooling air infiltrates into the spindle ball bearing, prevents leakage of lubricant to the outside of the bearing due to the cooling air and limits vibration of the cage by limiting turbulent flow of the cooling air inside the bearing. Provided is a spindle ball bearing 10, which: is provided with an inner ring 11 and an outer ring 12, multiple rolling elements 13 interposed between the inner ring and the outer ring, a cage 14 for holding the rolling elements, and a sealing member 15 for covering the opening of the gap between the inner ring and the outer ring; and is obtained by sealing a lubricant around the rolling elements. The sealing member 15 is provided with a mesh part 15a in a section that is located radially to the inside of the bore surface 14a of the cage 14.

Description

モータ内蔵スピンドル用玉軸受Ball bearing for spindle with built-in motor
　この発明は、小型スピンドル、特にモータ内蔵スピンドルに使用されるモータ内蔵スピンドル用玉軸受に関し、特に、内輪および外輪間に形成される軸受空間の端部開口を覆うシール部材を備えた玉軸受に関するものである。 The present invention relates to a ball bearing for a motor built-in spindle used in a small spindle, particularly a motor built-in spindle, and more particularly to a ball bearing provided with a seal member covering an end opening of a bearing space formed between an inner ring and an outer ring. It is.
　小型スピンドルは、主にアルミ加工などの軽負荷加工に用いられている。 Small spindle is mainly used for light load machining such as aluminum machining.
　近年、小型スピンドルは、図４に示すように、コンパクト化を目的にスピンドルのハウジング１内にモータ２を内蔵したタイプが多くなってきている（特許文献１）。なお、図４において、被加工物は、符号Ｗで示している。 In recent years, as shown in FIG. 4, many types of small spindles have a motor 2 incorporated in a spindle housing 1 for the purpose of compactness (Patent Document 1). In FIG. 4, the workpiece is indicated by the symbol W.
　この種のモータ内蔵スピンドル用玉軸受３としては、高速性を求められることから、アンギュラ玉軸受を使用することが多い。 As this kind of ball bearing 3 for a spindle with a built-in motor, an angular ball bearing is often used because high speed is required.
実用新案登録第３１５０３７１号公報Utility Model Registration No. 3150371
　モータ内蔵スピンドルは、スピンドルのハウジング１内にモータ２を内蔵していることから、モータ２の周辺が主な発熱源となるので、軸受３と共にモータ２を冷却する必要がある。 Since the spindle with a built-in motor has a motor 2 built in the housing 1 of the spindle, the periphery of the motor 2 becomes a main heat generation source, so the motor 2 needs to be cooled together with the bearing 3.
　スピンドルのハウジング１内を冷却する方法として液体又はエアオイルを用いた場合は、冷却液の漏出防止のためのシールが必要になる等、構造が複雑になるばかりか、スペース的にも問題が生じることが多い。 When liquid or air oil is used as a method of cooling the inside of the spindle housing 1, not only the structure is complicated, such as a seal for preventing leakage of the cooling liquid, but also there is a problem in space. There are many.
　このため、モータ内蔵スピンドルのハウジング１内の冷却には、複雑な構造が不要なエアでの冷却が主流になっている。 For this reason, the cooling in the housing 1 of the spindle with a built-in motor is mainly performed with air that does not require a complicated structure.
　このスピンドルのハウジング１内を冷却するエアは、スピンドルのハウジング１に設置された通気孔４により、後ろ側からモータ２、次に軸受３を冷却し、スピンドルのハウジング１の先端部１ａからスピンドルのハウジング１の外部に排出される。 The air that cools the inside of the spindle housing 1 cools the motor 2 and then the bearing 3 from the rear side by a vent hole 4 installed in the spindle housing 1, and the spindle housing 1 from the front end 1 a of the spindle 1 It is discharged outside the housing 1.
　スピンドルのハウジング１の先端部は、飛来物に対するシールを兼ねており、エアカーテン、ラビリンスシールにより、スピンドルのハウジング１の内部の圧力を高くし、切削液、加工片等がスピンドルのハウジング１内に侵入することを防止している。 The tip of the spindle housing 1 also serves as a seal against flying objects, and the pressure inside the spindle housing 1 is increased by an air curtain and a labyrinth seal so that cutting fluid, work pieces, etc. are contained in the spindle housing 1. Preventing intrusion.
　ところで、スピンドルのハウジング１内を冷却するエアは、軸受３の内部を通過するため、次のような問題がある。 Incidentally, since the air that cools the inside of the spindle housing 1 passes through the inside of the bearing 3, there is the following problem.
　モータ内蔵スピンドルに使用する軸受３は、内部に潤滑剤としてグリースが充填され、両端面がシール板によって密封されているが、スピンドルのハウジング１内を冷却するエアが軸受３の内部を通過すると、潤滑剤が外部に漏洩するおそれがある。この潤滑剤の漏洩は、軸受の耐久性能に影響を及ぼす可能性がある。 The bearing 3 used for the spindle with a built-in motor is filled with grease as a lubricant, and both end faces are sealed with seal plates. When air for cooling the inside of the spindle housing 1 passes through the inside of the bearing 3, Lubricant may leak to the outside. This leakage of the lubricant may affect the durability performance of the bearing.
　また、従来、シール板の内径部と、内輪の外径部との間は、ラビリンス構造になっているものがあり、当該ラビリンス構造により、軸受３の内部に侵入したエアの排出がシール板によって妨げられ、軸受３の内部に侵入したエアが軸受３の内部で乱流を引き起こして、保持器を振動させることがある。 Conventionally, there is a labyrinth structure between the inner diameter portion of the seal plate and the outer diameter portion of the inner ring, and by the labyrinth structure, discharge of air that has entered the inside of the bearing 3 is caused by the seal plate. Air that has been blocked and has entered the inside of the bearing 3 may cause turbulence inside the bearing 3 and cause the cage to vibrate.
　保持器の振動は、スピンドルのハウジング１に振動が伝達され、加工精度や静粛性にも悪影響を及ぼす。 The vibration of the cage is transmitted to the spindle housing 1 and adversely affects machining accuracy and quietness.
　そこで、この発明は、モータ内蔵スピンドルの軸受内に冷却エアが侵入した際に、冷却エアによる潤滑剤の軸受外部へ漏洩を防止し、また、冷却エアの軸受内部での乱流を抑制して保持器の振動を抑え、静粛性の高いピンドル用玉軸受を提供しようとするものである。 Therefore, the present invention prevents leakage of lubricant to the outside of the bearing due to cooling air when cooling air enters the bearing of the spindle with a built-in motor, and suppresses turbulent flow of cooling air inside the bearing. The purpose of the present invention is to provide a pindle ball bearing that suppresses the vibration of the cage and is highly quiet.
　上記の課題を解決するため、この発明においては、内輪および外輪と、この内輪および外輪間に介在する複数の転動体と、転動体を保持する保持器と、前記内輪および外輪間の隙間の開口を覆うシール部材とを備え、前記転動体の周囲に潤滑剤を封入してなるスピンドル用玉軸受であって、
　前記シール部材は、少なくとも一部分に気体透過性のメッシュ状部を備えていることを特徴とする。 In order to solve the above-described problems, in the present invention, an inner ring and an outer ring, a plurality of rolling elements interposed between the inner ring and the outer ring, a cage that holds the rolling elements, and an opening of a gap between the inner ring and the outer ring And a ball bearing for spindle formed by sealing a lubricant around the rolling element,
The seal member includes a gas-permeable mesh portion at least partially.
　また、前記メッシュ状部は、前記保持器の内径面よりも内径側に位置する部分に設けるようにしてもよい。 Further, the mesh portion may be provided in a portion located on the inner diameter side of the inner diameter surface of the cage.
　さらに、前記シール部材は、前記メッシュ状部を構成するメッシュ部材と、前記メッシュ部材に積層して設けられ前記外輪に装着される支持部材とを備え、前記メッシュ部材は、前記支持部材より内径側に突出して設けられることで、当該突出部分をメッシュ状部とすることができる。また、好適には、メッシュ部材は、合成樹脂繊維の不織布で構成することができる。 Further, the seal member includes a mesh member constituting the mesh-like portion, and a support member provided on the mesh member so as to be attached to the outer ring, and the mesh member has an inner diameter side than the support member. By projecting to the surface, the projecting portion can be a mesh-shaped portion. Preferably, the mesh member can be composed of a nonwoven fabric of synthetic resin fibers.
　この発明に係るスピンドル用玉軸受においては、上記のように、シール板の少なくとも一部分をメッシュ状部としているため、軸受内に潤滑剤を保持しつつ、冷却エアなどの気体を透過するメッシュ状部によって冷却エアを軸受外部に通過させることが可能となる。このため、安定したシール性と冷却エアの軸受内透過性をそれぞれ確保でき、潤滑剤が外部へ漏洩したり、冷却エアの乱流による保持器の振動などを防止することができる。したがって、軸受寿命と音響性能の両立が可能となる。 In the spindle ball bearing according to the present invention, as described above, since at least a part of the seal plate is a mesh-like portion, a mesh-like portion that allows a gas such as cooling air to pass through while retaining the lubricant in the bearing. This allows the cooling air to pass outside the bearing. For this reason, stable sealing performance and permeability of the cooling air in the bearing can be ensured, respectively, and the lubricant can be leaked to the outside or the cage vibration due to the turbulent flow of the cooling air can be prevented. Therefore, both bearing life and acoustic performance can be achieved.
　さらに、メッシュ状部を保持器の内径面よりも内径側に配置させることにより、エアの通過がよりスムーズに行われる。 Furthermore, air can be passed more smoothly by disposing the mesh-shaped portion closer to the inner diameter side than the inner diameter surface of the cage.
この発明の実施形態に係るスピンドル用玉軸受の部分断面図である。It is a fragmentary sectional view of the ball bearing for spindles concerning the embodiment of this invention. 図１のモータ内蔵スピンドル用玉軸受の部分拡大図である。It is the elements on larger scale of the ball bearing for spindles with a built-in motor of FIG. 本発明の他の実施形態に係るモータ内蔵スピンドル用玉軸受の部分断面図である。It is a fragmentary sectional view of the ball bearing for spindles with a built-in motor concerning other embodiments of the present invention. モータ内蔵スピンドルの概略図である。It is the schematic of a spindle with a built-in motor.
　以下、この発明の実施の形態を添付図面に基づいて説明する。この発明の一実施形態に係るモータ内蔵スピンドル用玉軸受は、図１に示すように、アンギュラ玉軸受である。 Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. As shown in FIG. 1, the ball bearing for spindle with a built-in motor according to one embodiment of the present invention is an angular ball bearing.
　この発明に係るアンギュラ玉軸受１０は、内輪１１と、外輪１２と、内輪１１と外輪１２の対向する転動面に配設された転動体１３と、転動体１３を保持する保持器１４と、内輪１１と外輪１２の両端面に設けられ内外輪間の隙間の開口を覆うシール板１５とを有する。内輪１１と外輪１２との間の空間には、潤滑剤としてグリースが充填されており、シール板１５により外部への漏出が防止される。 An angular ball bearing 10 according to the present invention includes an inner ring 11, an outer ring 12, rolling elements 13 disposed on the rolling surfaces facing the inner ring 11 and the outer ring 12, a cage 14 that holds the rolling elements 13, A seal plate 15 is provided on both end faces of the inner ring 11 and the outer ring 12 and covers an opening of a gap between the inner and outer rings. The space between the inner ring 11 and the outer ring 12 is filled with grease as a lubricant, and leakage to the outside is prevented by the seal plate 15.
　また、本実施形態では、外輪１２の軌道輪と転動体１３との間、外輪１２の軌道輪と保持器１４との間に、安定的に潤滑剤を供給するため、外輪１２の一部にグリースポケット２０を設けている。 In the present embodiment, a lubricant is stably supplied between the raceway of the outer ring 12 and the rolling element 13, and between the raceway of the outer ring 12 and the cage 14. A grease pocket 20 is provided.
　潤滑剤であるグリースは、静止空間容積の４０％～５０％程度封入することが好ましい。４０％以下の場合、エア圧よるグリースの偏りにより、安定した耐久効果が得られにくい。５０％以上の場合、エア圧よるグリースの偏りにより、グリースの再巻き込み過多により温度変動大、振動変動に繋がり安定した回転が得られない。なお、グリースの基油粘度は、２０～４０ｍｍ2/ｓが好ましい。 The grease, which is a lubricant, is preferably enclosed by about 40% to 50% of the static space volume. In the case of 40% or less, it is difficult to obtain a stable durability effect due to the bias of grease due to air pressure. In the case of 50% or more, due to grease bias due to air pressure, excessive rewinding of grease leads to large temperature fluctuations and vibration fluctuations, and stable rotation cannot be obtained. The base oil viscosity of the grease is preferably 20 to 40 mm 2 / s.
　外輪１２の内径面には、軸方向の両端部に取付溝１６が設けられており、当該取付溝１６にシール板１５の外周部が支持されている。 The inner ring surface of the outer ring 12 is provided with mounting grooves 16 at both ends in the axial direction, and the outer peripheral portion of the seal plate 15 is supported by the mounting grooves 16.
　図１および図２に示すように、シール板１５は、その内周部が内輪１１の外周面１１ａと小さな径方向間隙をおいて対向する。本実施形態では、シール板１５の内径部と対面する内輪１１の外径面１１ａは、図１及び図２に示すように、直線状に形成され、シール板１５の内径部と内輪１１の外径面との間に、ラビリンス構造を形成するシール溝を形成していない。 As shown in FIGS. 1 and 2, the seal plate 15 has its inner peripheral portion opposed to the outer peripheral surface 11a of the inner ring 11 with a small radial gap. In the present embodiment, the outer diameter surface 11a of the inner ring 11 facing the inner diameter portion of the seal plate 15 is formed in a straight line as shown in FIGS. A seal groove for forming a labyrinth structure is not formed between the radial surface and the radial surface.
　シール板１５はメッシュ部材１７と支持部材１８の２種類の板状部材を積層した構成となっている。シール板１５は、メッシュ部材１７と支持部材１８が積層した状態となっており、一例としてインサート成型により製造される。 The seal plate 15 has a configuration in which two types of plate members, a mesh member 17 and a support member 18, are laminated. The seal plate 15 is in a state where the mesh member 17 and the support member 18 are laminated, and is manufactured by insert molding as an example.
　図１及び図２に示すように、シール板１５の軸方向内側に位置するメッシュ部材１７は、合成樹脂繊維を編製や織製などの手段でシート状にし、気体透過性を有するメッシュ構造を有する部材である。本実施形態では、合成樹脂繊維の不織布製フィルターが使用されている。 As shown in FIGS. 1 and 2, the mesh member 17 located on the inner side in the axial direction of the seal plate 15 has a mesh structure having a gas permeability by forming synthetic resin fibers into a sheet shape by means of knitting or weaving. It is a member. In this embodiment, a synthetic resin fiber non-woven fabric filter is used.
　メッシュ部材１７は、圧力損失が５０％程度に構成されていることが好ましく、冷却エアのみを通過させるように構成されている。また、メッシュ部材を構成する合成樹脂は、グリースとの相性がよいものであって、グリースとケミカルアタックしない、又は体積変化率が１０％以下のものを用いることが好ましい。 The mesh member 17 is preferably configured to have a pressure loss of about 50%, and is configured to allow only cooling air to pass through. The synthetic resin constituting the mesh member is preferably compatible with grease and does not chemically attack the grease, or has a volume change rate of 10% or less.
　シール板１５の軸方向外側には、支持部材１８が設けられている。支持部材１８は、外輪への装着性を考慮してゴム又は合成樹脂で構成されており、可撓性を有するメッシュ部材１７を支持する。支持部材１８は、メッシュ部材１７の支持と外輪への装着性のために設けられるものであり、これらを具現化できるものであれば、その構成は問わない。例えば、支持部材１８は、メッシュ部材１７を積層支持する箇所に、空気を透過することができる貫通孔などを設けることもできる。 A support member 18 is provided outside the seal plate 15 in the axial direction. The support member 18 is made of rubber or synthetic resin in consideration of the mounting property to the outer ring, and supports the mesh member 17 having flexibility. The support member 18 is provided to support the mesh member 17 and to be attached to the outer ring, and the configuration thereof is not limited as long as these can be embodied. For example, the support member 18 can also be provided with a through hole or the like through which air can permeate at a location where the mesh member 17 is laminated and supported.
　また、メッシュ部材１７は、支持部材１８よりも内輪側に突出した状態に設けられ、当該突出部分がメッシュ状部１５ａとなっている。メッシュ状部１５ａは、空気透過性材料であるメッシュ部材１７のみが配置されているため、冷却エアを通過させることができる。 Further, the mesh member 17 is provided in a state of projecting to the inner ring side from the support member 18, and the projecting portion is a mesh-shaped portion 15a. Since only the mesh member 17 that is an air permeable material is disposed in the mesh-like portion 15a, the cooling air can be passed therethrough.
　メッシュ部材１７が支持部材１８よりも内輪側に突出したメッシュ状部１５ａは、保持器１４の内径面１４ａよりも内径側に位置することが好ましい。 It is preferable that the mesh-like portion 15 a in which the mesh member 17 protrudes to the inner ring side from the support member 18 is located on the inner diameter side from the inner diameter surface 14 a of the cage 14.
　このように構成することにより、通過するエアの入口側から出口側に向かって、冷却エアが保持器１４の抵抗を受けることなく通過できる。また、本実施形態では、内輪１１の外周面１１ａも直線的に設けられているため、出口側の内輪１１の外径面とシール板１５のメッシュ状部１５ａとの間の隙間の投影面積が、軸受を通過するエア流路の通過投影面積とほぼ同等になる。 With this configuration, the cooling air can pass without receiving the resistance of the cage 14 from the inlet side to the outlet side of the passing air. In this embodiment, since the outer peripheral surface 11a of the inner ring 11 is also provided linearly, the projected area of the gap between the outer diameter surface of the inner ring 11 on the outlet side and the mesh-like portion 15a of the seal plate 15 is increased. This is almost the same as the projected projection area of the air flow path passing through the bearing.
　シール板１５のメッシュ状部１５ａからシール板１５に対面する内輪１１の外径面との間が、上記のように、エアが抵抗なくほぼ直線状に通過できる投影面積になるように、シール板１５を規定することにより、軸受の内部をエアが通過する際に、シール板１５に余分な力が加わり難く、シール板１５の倒れや変形を防止し、安定したシール性を確保できる。また、保持器１４の内径面よりも内径側にメッシュ状部１５ａが存在しているため、軸受内部のグリースの漏洩も防止される。 As described above, the seal plate has a projected area through which air can pass substantially linearly without resistance between the mesh-like portion 15a of the seal plate 15 and the outer diameter surface of the inner ring 11 facing the seal plate 15. By defining 15, when air passes through the inside of the bearing, it is difficult for excessive force to be applied to the seal plate 15, preventing the seal plate 15 from falling and deforming, and ensuring a stable sealing property. Further, since the mesh-shaped portion 15a exists on the inner diameter side of the inner diameter surface of the cage 14, leakage of grease inside the bearing is also prevented.
　なお、上記実施形態では、シール板１５の内径部と対面する内輪１１の外径面１１ａを直線状に形成しているが、例えば、図３に示すように、シール板１５の内径部と内輪１１の外径面との間に、ラビリンス構造を形成するシール溝１９を設けてもよく、グリースの密封性を向上させることができる。 In the above embodiment, the outer diameter surface 11a of the inner ring 11 facing the inner diameter portion of the seal plate 15 is formed in a straight line. For example, as shown in FIG. A seal groove 19 that forms a labyrinth structure may be provided between the outer diameter surface of 11 and the sealability of grease can be improved.
　上記の通り、本実施形態では、軸受内部の潤滑剤を保持しつつ冷却エアの通過をより妨げないようにするため、軸受寿命と音響性能の両立が可能となる。 As described above, in this embodiment, both the bearing life and the acoustic performance can be achieved in order to prevent the passage of the cooling air while holding the lubricant inside the bearing.
　以上、図面を参照してこの発明の実施形態を説明したが、この発明は、図示した実施形態のものに限定されない。図示した実施形態に対して、この発明と同一の範囲内において、あるいは均等の範囲内において、種々の修正や変形を加えることが可能である。 As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.
　例えば、本発明は、アンギュラ玉軸受に限定されるものではなく、シール板を有する他の構成の玉軸受や組み合わせ玉軸受にも適用可能である。また、本実施形態では、シール板の撓みなどの問題が生じるため、ゴムや樹脂製の支持部材をメッシュ部材に積層して用いているが、シール板は、部分的又は全体的にメッシュ状部が設けられ、当該メッシュ状部が気体透過性を有するものであればよい。たとえば、全体をメッシュ部材で構成することもできる。また、このとき例えば、メッシュ部材の補強のための支持骨組みをメッシュ部材中に埋設してもよい。 For example, the present invention is not limited to angular contact ball bearings, but can be applied to other types of ball bearings or combination ball bearings having a seal plate. In this embodiment, since problems such as bending of the seal plate occur, a rubber or resin support member is laminated on the mesh member. However, the seal plate is partially or entirely mesh-shaped. As long as the mesh-shaped part has gas permeability. For example, the whole can be configured by a mesh member. At this time, for example, a support framework for reinforcing the mesh member may be embedded in the mesh member.
１１　　　：内輪
１１ａ　　：外径面
１２　　　：外輪
１３　　　：転動体
１４　　　：保持器
１４ａ　　：内径面
１５　　　：シール板
１５ａ　　：メッシュ状部
１６　　　：取付溝
１７　　　：メッシュ部材
１８　　　：支持部材
１９　　　：シール溝
２０　　　：グリースポケット 11: Inner ring 11a: Outer diameter surface 12: Outer ring 13: Rolling element 14: Cage 14a: Inner diameter surface 15: Seal plate 15a: Mesh-like portion 16: Mounting groove 17: Mesh member 18: Support member 19: Seal groove 20: Grease pocket

Claims (4)

  1. 　内輪および外輪と、この内輪および外輪間に介在する複数の転動体と、転動体を保持する保持器と、前記内輪および外輪間の隙間の開口を覆うシール部材とを備え、前記転動体の周囲に潤滑剤を封入してなるスピンドル用玉軸受であって、
    　前記シール部材は、少なくとも一部分に気体透過性のメッシュ状部を備えていることを特徴とする、スピンドル用玉軸受。     An inner ring and an outer ring; a plurality of rolling elements interposed between the inner ring and the outer ring; a cage that holds the rolling element; and a seal member that covers an opening of a gap between the inner ring and the outer ring; A ball bearing for a spindle in which a lubricant is sealed in,
    A ball bearing for a spindle, wherein the seal member includes a gas-permeable mesh portion at least partially.
  2. 　前記メッシュ状部は、前記保持器の内径面よりも内径側に位置する部分に設けられていることを特徴とする、請求項１に記載のスピンドル用玉軸受。 The spindle ball bearing according to claim 1, wherein the mesh-shaped portion is provided in a portion located on an inner diameter side of the inner diameter surface of the cage.
  3. 　前記シール部材は、前記メッシュ状部を構成するメッシュ部材と、前記メッシュ部材に積層して設けられ前記外輪に装着される支持部材とを備え、前記メッシュ部材は、前記支持部材より内径側に突出して設けられることで、当該突出部分がメッシュ状部となることを特徴とする、請求項１又は２に記載のスピンドル用玉軸受。 The seal member includes a mesh member that forms the mesh-like portion, and a support member that is stacked on the mesh member and is attached to the outer ring, and the mesh member protrudes toward the inner diameter side from the support member. The spindle ball bearing according to claim 1, wherein the protruding portion becomes a mesh-like portion.
  4. 　前記メッシュ部材は、合成樹脂繊維の不織布で構成されていることを特徴とする、請求項３に記載のスピンドル用玉軸受。 The spindle ball bearing according to claim 3, wherein the mesh member is made of a nonwoven fabric of synthetic resin fibers.
PCT/JP2017/001926 2016-02-01 2017-01-20 Ball bearing for spindle with built-in motor WO2017135073A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023233649A1 (en) * 2022-06-03 2023-12-07 株式会社ジェイテクト Sliding member and rolling bearing

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5597378U (en) * 1978-12-28 1980-07-07
JPH0348518U (en) * 1989-09-18 1991-05-09
JP2003097565A (en) * 2001-09-25 2003-04-03 Nsk Ltd Angular ball bearing
JP2005226675A (en) * 2004-02-10 2005-08-25 Ntn Corp Sealed roller bearing
WO2009125734A1 (en) * 2008-04-08 2009-10-15 Nok株式会社 Sealing device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5597378U (en) * 1978-12-28 1980-07-07
JPH0348518U (en) * 1989-09-18 1991-05-09
JP2003097565A (en) * 2001-09-25 2003-04-03 Nsk Ltd Angular ball bearing
JP2005226675A (en) * 2004-02-10 2005-08-25 Ntn Corp Sealed roller bearing
WO2009125734A1 (en) * 2008-04-08 2009-10-15 Nok株式会社 Sealing device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023233649A1 (en) * 2022-06-03 2023-12-07 株式会社ジェイテクト Sliding member and rolling bearing

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