JP2013092242A - Retainer for deep groove ball bearing, deep groove ball bearing using the retainer, and bearing device - Google Patents

Retainer for deep groove ball bearing, deep groove ball bearing using the retainer, and bearing device Download PDF

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JP2013092242A
JP2013092242A JP2011236051A JP2011236051A JP2013092242A JP 2013092242 A JP2013092242 A JP 2013092242A JP 2011236051 A JP2011236051 A JP 2011236051A JP 2011236051 A JP2011236051 A JP 2011236051A JP 2013092242 A JP2013092242 A JP 2013092242A
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cage
deep groove
diameter
retainer
split
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Yasunari Tomura
泰成 戸村
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3862—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together
    • F16C33/3875—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together made from plastic, e.g. two injection moulded parts joined by a snap fit
    • 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
    • F16C33/38—Ball cages
    • F16C33/3887—Details of individual pockets, e.g. shape or ball retaining means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/36—Polyarylene ether ketones [PAEK], e.g. PEK, PEEK
    • 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
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/52—Polyphenylene sulphide [PPS]
    • 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
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/60—Polyamides [PA]
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips

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

Abstract

PROBLEM TO BE SOLVED: To provide a retainer for a deep groove ball bearing capable of reducing stagnation of a foreign substance inside the bearing and a torque loss and improving oil passing properties.SOLUTION: A taper angle of a first divided retainer 41 formed in a taper shape and a taper angle of a second divided retainer 42 formed in a taper shape are the same. Outer and inner diameters of a large-diameter end surface of the first divided retainer 41 and outer and inner diameters of a small-diameter end surface of the second divided retainer 42 are the same. A plurality of semicircular pockets 43 are equidistantly formed at a large-diameter end of the first divided retainer 41. A plurality of semicircular pockets 44 forming, together with the pockets 43 of the first divided retainer 41, circular pockets 45 are equidistantly formed at a small-diameter end of the second divided retainer 42. An engagement claw 47 is provided at a pillar part 46 between the pockets 43 of the first divided retainer 41. The engagement claw 47 is engaged with an engagement recess 49 formed at a pillar part 48 between the pockets 44 of the second divided retainer 42 to connect the first divided retainer 41 and the second divided retainer 42 in the axial direction so that the retainer 40 of the taper shape is assembled.

Description

この発明は、深みぞ玉軸受用の保持器およびその保持器を用いた深みぞ玉軸受ならびに軸受装置に関する。   The present invention relates to a deep groove ball bearing retainer, a deep groove ball bearing using the retainer, and a bearing device.

インプットシャフトとアウトプットシャフトを同軸上に配置し、その両軸に平行にカウンタシャフトを設け、その平行する２軸の相互間に変速比の異なる複数の歯車式減速部を設けて、インプットシャフトの回転を複数段に変速してアウトプットシャフトから出力するようにしたトランスミッションにおいては、一般的に、歯車式減速部にヘリカルギヤを採用しているため、インプットシャフトからアウトプットシャフトへの回転トルクの伝達時、インプットシャフト、アウトプットシャフトおよびカウンタシャフトのそれぞれにスラスト力が負荷されることになる。   The input shaft and the output shaft are arranged on the same axis, the countershaft is provided in parallel to both axes, and a plurality of gear-type reduction gears with different gear ratios are provided between the two parallel axes to rotate the input shaft. In a transmission that shifts to multiple stages and outputs from the output shaft, a helical gear is generally used for the gear-type reduction gear, so input torque is transmitted from the input shaft to the output shaft. A thrust force is applied to each of the shaft, the output shaft, and the counter shaft.

このため、インプットシャフト、アウトプットシャフトおよびカウンタシャフトを支持する軸受には、ラジアル荷重とスラスト荷重の両方の荷重を支持することができる軸受を用いる必要がある。   For this reason, it is necessary to use a bearing that can support both a radial load and a thrust load as a bearing that supports the input shaft, the output shaft, and the counter shaft.

円すいころ軸受においては、負荷容量が大きく、スラスト荷重およびラジアル荷重の両方を受けることができるため、トランスミッション用軸受に好適である。しかし、円すいころ軸受においては、損失トルクが大きく、燃料の消費量が多くなるという問題が生じる。その低燃費化を図るため、損失トルクの少ない深みぞ玉軸受が使用されるケースが多くなってきている。   Tapered roller bearings are suitable for transmission bearings because they have a large load capacity and can receive both thrust loads and radial loads. However, in the tapered roller bearing, there is a problem that the loss torque is large and the amount of fuel consumption increases. In order to reduce fuel consumption, there are many cases where deep groove ball bearings with less loss torque are used.

ところで、標準の深みぞ玉軸受においては、過大なスラスト荷重が負荷された際に、そのスラスト荷重を受ける負荷側の肩にボールが乗り上げて、肩のエッジが損傷する懸念がある。   By the way, in a standard deep groove ball bearing, when an excessive thrust load is applied, there is a concern that the ball rides on the load-side shoulder receiving the thrust load and the shoulder edge is damaged.

そのような不都合を解消するため、特許文献１に記載された深みぞ玉軸受においては、外輪の軌道溝および内輪の軌道溝のそれぞれ両側に形成された肩のうち、スラスト荷重を受ける側の肩を高くして、ボールの乗り上げを阻止し、軸受の耐久性の低下を抑制するようにしている。   In order to eliminate such inconvenience, in the deep groove ball bearing described in Patent Document 1, of the shoulders formed on both sides of the outer ring raceway groove and the inner ring raceway groove, the shoulder on the side receiving the thrust load. Is increased to prevent the ball from climbing and to suppress a decrease in the durability of the bearing.

特開２０１１−７２８６号公報JP 2011-7286 A

ところで、上記特許文献１に記載された深みぞ玉軸受においては、内輪および外輪の肩高さが左右非対称であるため、径の異なる２つの分割保持器を内外に嵌合し、一方の分割保持器に形成された係合爪を他方の分割保持器に設けられた係合凹部に係合させて、一対の分割保持器を軸方向に結合してボールを保持する保持器を形成するようにしているため、保持器の外径面および内径面に多くの凹凸部が形成され、その凹凸部にギヤの摩耗粉等の異物が付着滞留し易く、また、潤滑オイルが撹拌されることになってトルク損失が多く、異物の滞留やトルク損失の低減を図る上においても改善すべき点が残されていた。   By the way, in the deep groove ball bearing described in Patent Document 1, since the shoulder heights of the inner ring and the outer ring are asymmetrical, two divided cages having different diameters are fitted inside and outside, and one divided holding is performed. The engaging claw formed on the container is engaged with the engaging recess provided on the other divided holder, and the pair of divided holders are coupled in the axial direction to form a holder for holding the ball. Therefore, many irregularities are formed on the outer diameter surface and inner diameter surface of the cage, and foreign matters such as gear wear powder are liable to adhere and stay on the irregularities, and the lubricating oil is agitated. Therefore, there are many torque losses, and there are still points to be improved in order to reduce foreign matter retention and torque loss.

また、大径側分割保持器と小径側分割保持器の外径面間および内径面間に径方向の段差が形成されるため、その段差で潤滑オイルの流れが阻害されて軸受内部に潤滑オイルをスムーズに流通させることができず、通油性を向上させる上において改善すべき点が残されていた。   In addition, since a radial step is formed between the outer diameter surface and the inner diameter surface of the large-diameter side split cage and the small-diameter side split cage, the flow of the lubricating oil is obstructed by the step, and the lubricating oil is contained inside the bearing. Cannot be smoothly distributed, and there are still points to be improved in improving oil permeability.

この発明の課題は、軸受内部での異物の滞留およびトルク損失の低減と通油性の向上を図ることができる深みぞ玉軸受用保持器および深みぞ玉軸受ならびに軸受装置を提供することである。   An object of the present invention is to provide a deep groove ball bearing retainer, a deep groove ball bearing, and a bearing device capable of reducing the retention of foreign matters in the bearing, reducing torque loss, and improving oil permeability.

上記の課題を解決するため、この発明に係る深みぞ玉軸受用保持器においては、テーパ状とされた第１分割保持器と、その第１分割保持器とテーパ角度が同じとされて、小径端面の外径および内径が第１分割保持器の大径端面の外径および内径と同径とされたテーパ状の第２分割保持器とからなり、前記第１分割保持器の大径端と第２分割保持器の小径端のそれぞれに、第１分割保持器の大径端面に第２分割保持器の小径端面を衝合させる接続状態でボール収容用の円形のポケットを形成する複数の半円形ポケットを周方向に等間隔に設け、前記第１分割保持器の半円形ポケット間に形成された柱部の端面と第２分割保持器の半円形ポケット間に形成された柱部の端面の、一方の端面の外周部または内周部に、先端が鈎部とされた係合爪を設け、他方の端面に、その係合爪が係合可能とされ、係合状態で第１分割保持器と第２分割保持器とを軸方向に結合する係合凹部を設けた構成を採用したのである。   In order to solve the above-mentioned problem, in the deep groove ball bearing retainer according to the present invention, the tapered first divided retainer and the taper angle of the first divided retainer are the same, and the small diameter A tapered second split cage whose outer diameter and inner diameter of the end surface are the same as the outer diameter and inner diameter of the large diameter end surface of the first split cage, and the large diameter end of the first split cage; A plurality of half-shaped pockets are formed in each of the small-diameter ends of the second split cage so as to form a circular pocket for accommodating a ball in a connected state in which the small-diameter end surface of the second split cage is brought into contact with the large-diameter end surface of the first split cage. Circular pockets are provided at equal intervals in the circumferential direction, and the end surfaces of the column portions formed between the semicircular pockets of the first divided cage and the semicircular pockets of the second divided cage are arranged. An engaging claw whose tip is a hook is provided on the outer peripheral part or inner peripheral part of one end face. Since the engaging claw can be engaged with the other end surface, and the engaging concave portion for connecting the first divided holder and the second divided holder in the axial direction in the engaged state is adopted. is there.

また、この発明に係る深みぞ玉軸受においては、内径面に軌道溝が形成された外輪と、外径面に軌道溝が形成された内輪と、外輪の軌道溝と内輪の軌道溝間に組込まれたボールと、そのボールを保持する保持器とからなり、前記外輪軌道溝の一側の肩と内輪軌道溝の他側の肩の少なくとも一方の高さを、外輪軌道溝の他側の肩または内輪軌道溝の一側の肩の高さより高くし、その高さの高い肩の肩高さをＨ１、ボールの球径をｄとしたとき、ボールの球径ｄに対する肩高さＨ１の比率Ｈ１／ｄを０．２５〜０．５０の範囲とした深みぞ玉軸受において、前記保持器として、この発明に係る上記構成の保持器を採用したのである。 Further, in the deep groove ball bearing according to the present invention, the outer ring having the raceway groove formed on the inner diameter surface, the inner ring having the raceway groove formed on the outer diameter surface, and the raceway groove of the outer ring and the raceway groove of the inner ring are incorporated. And a retainer for holding the ball. The height of at least one of the shoulder on one side of the outer ring raceway groove and the shoulder on the other side of the inner ring raceway groove is set to the shoulder on the other side of the outer ring raceway groove. Alternatively, when the height of the shoulder on one side of the inner ring raceway groove is made higher, the shoulder height of the higher shoulder is H 1 , and the ball diameter of the ball is d, the shoulder height H 1 with respect to the ball diameter d of the ball. In the deep groove ball bearing in which the ratio H 1 / d is in the range of 0.25 to 0.50, the cage having the above-described configuration according to the present invention is employed as the cage.

上記の構成からなる深みぞ玉軸受の組立てに際しては、外輪と内輪の軌道溝間に複数のボールを組み込んだのち、外輪と内輪の対向部間に第１分割保持器および第２分割保持器を挿入する。   When assembling the deep groove ball bearing having the above-described configuration, a plurality of balls are assembled between the raceway grooves of the outer ring and the inner ring, and then the first split cage and the second split cage are placed between the opposing portions of the outer ring and the inner ring. insert.

このとき、第１分割保持器は、外輪の高さの高い肩側からポケット形成側端を先にして対向部間に挿入し、一方、第２分割保持器は、外輪の高さの低い肩側からポケット形成側端を先にして対向部間に挿入し、一方の分割保持器に形成された係合爪が他方の分割保持器に設けられた係合凹部に軸方向で対向し、かつ、半円形ポケットがボールと軸方向で対向するよう、第１および第２の分割保持器の向きを調整して、その第１および第２の分割保持器を軸方向に押し込むようにする。   At this time, the first split cage is inserted between the opposing portions with the pocket forming side end first from the shoulder side where the height of the outer ring is high, while the second split cage is the shoulder where the height of the outer ring is low The pocket forming side end first is inserted between the opposing portions from the side, and the engaging claws formed in one of the split holders are axially opposed to the engaging recesses provided in the other split holder, and The direction of the first and second split cages is adjusted so that the semicircular pocket faces the ball in the axial direction, and the first and second split cages are pushed in in the axial direction.

上記のように、第１および第２の分割保持器の向きを調整して、双方の分割保持器を軸方向に押し込むことにより、係合爪が相手方の分割保持器の係合凹部に係合し、第１分割保持器と第２分割保持器が互いに結合されて保持器が形成され、複数のボールは円形に組み合わされたポケットのそれぞれで保持されて、深みぞ玉軸受が組立状態とされる。   As described above, by adjusting the orientation of the first and second split cages and pushing both split cages in the axial direction, the engaging claws engage with the engaging recesses of the other split cage. The first divided cage and the second divided cage are combined with each other to form a cage, and the plurality of balls are held in the circularly combined pockets, and the deep groove ball bearing is in an assembled state. The

ここで、保持器を形成する第１分割保持器と第２分割保持器はテーパ状とされ、第１分割保持器の大径端面の外径および内径が第２分割保持器の小径端面の外径および内径と同径であるため、外表面および内表面に段差のないテーパ状の保持器を組み立てることができる。そのため、その保持器を用いて深みぞ玉軸受を組み立てることにより、軸受内部に侵入する異物が保持器の表面に付着して滞留することが少なく、異物の滞留を低減することができる。   Here, the first divided cage and the second divided cage forming the cage are tapered, and the outer diameter and inner diameter of the large-diameter end surface of the first divided cage are outside the small-diameter end surface of the second divided cage. Since the diameter is the same as the inner diameter, a tapered cage having no steps on the outer surface and the inner surface can be assembled. Therefore, by assembling the deep groove ball bearing using the cage, foreign matter that enters the bearing is less likely to adhere to and stay on the surface of the cage, and the retention of foreign matter can be reduced.

また、保持器は、テーパ状をなし、大径端と小径端は径差を有するため、保持器の回転時、大径端部と小径端部の周速差によってポンプ作用が生じ、軸受空間内に潤滑オイルが送り込まれることになる。このとき、保持器は、その外表面および内表面が滑らかであるため、潤滑オイルはスムーズに流れ、また、潤滑オイルの撹拌抵抗も小さく、トルク損失も少ない。   In addition, the cage is tapered, and the large diameter end and the small diameter end have a difference in diameter. Therefore, when the cage rotates, a pumping action is generated due to a difference in peripheral speed between the large diameter end and the small diameter end. Lubricating oil will be fed into the inside. At this time, since the outer surface and the inner surface of the cage are smooth, the lubricating oil flows smoothly, the stirring resistance of the lubricating oil is small, and the torque loss is small.

ここで、第１分割保持器および第２分割保持器は、低コスト化を図るため、合成樹脂の成形品とするのが好ましい。この場合、深みぞ玉軸受は、オイル潤滑されるため、耐油性および耐久性に優れた合成樹脂で成形するのが好ましい。そのような樹脂として、ポリアミド４６（ＰＡ４６）、ポリアミド６６（ＰＡ６６）、ポリアミド９Ｔ(ＰＡ９Ｔ)、ポリエーテルエーテルケトン樹脂(ＰＥＥＫ)、ポリフェニレンサルファイド樹脂(ＰＰＳ)を挙げることができる。それらの樹脂のうち、ポリフェニレンスルファイド（ＰＰＳ）は、他の樹脂に比較して耐油性が優れているため、耐油性を考慮するならば、ポリフェニレンスルファイド（ＰＰＳ）を用いるのが最も好ましい。   Here, it is preferable that the first split cage and the second split cage are molded products of synthetic resin in order to reduce costs. In this case, since the deep groove ball bearing is oil-lubricated, it is preferable to mold it with a synthetic resin having excellent oil resistance and durability. Examples of such resins include polyamide 46 (PA46), polyamide 66 (PA66), polyamide 9T (PA9T), polyetheretherketone resin (PEEK), and polyphenylene sulfide resin (PPS). Among these resins, polyphenylene sulfide (PPS) has excellent oil resistance compared to other resins, and therefore, considering the oil resistance, it is most preferable to use polyphenylene sulfide (PPS).

また、樹脂材料の価格を考慮するならば、ポリアミド６６（ＰＡ６６）を用いるのが好ましく、潤滑オイルの種類に応じて適宜に決定すればよい。   In view of the price of the resin material, it is preferable to use polyamide 66 (PA66), which may be determined appropriately according to the type of the lubricating oil.

この発明に係る軸受装置においては、ヘリカルギヤが設けられたシャフトを油浴に一部が浸かる一対の転がり軸受で回転自在に支持した軸受装置において、前記一対の転がり軸受として、この発明に係る上記の深みぞ玉軸受を用いた構成としたのである。   In the bearing device according to the present invention, in the bearing device in which a shaft provided with a helical gear is rotatably supported by a pair of rolling bearings partially immersed in an oil bath, the pair of rolling bearings described above is used as the pair of rolling bearings. The structure uses a deep groove ball bearing.

この発明に係る深みぞ玉軸受用保持器においては、上記のように、テーパ状の第１分割保持器と第２分割保持器とを、そのテーパ角度を同一とし、第１分割保持器の大径端面の外径および内径を第２分割保持器の小径端面の外径および内径と同径とし、その第１分割保持器と第２分割保持器とを、係合爪と係合凹部の係合により軸方向に結合してテーパ状としたので、外輪の左右の肩高さおよび内輪の左右の肩高さを相違させて大きなスラスト荷重やラジアル荷重を受けることができるようにした深みぞ玉軸受に適用することができる。   In the deep groove ball bearing retainer according to the present invention, as described above, the tapered first split retainer and the second split retainer have the same taper angle, and the first split retainer is large. The outer diameter and inner diameter of the radial end surface are the same as the outer diameter and inner diameter of the small-diameter end surface of the second split retainer, and the first split retainer and the second split retainer are connected to the engagement claw and the engagement recess. A deep groove ball that can be combined with the axial direction and tapered so that it can receive large thrust loads and radial loads by making the left and right shoulder height of the outer ring different from the left and right shoulder height of the inner ring. It can be applied to bearings.

また、第１分割保持器と第２分割保持器の結合によって組み立てられた保持器は、段差のない滑らかなテーパ状外表面およびテーパ状内表面を形成するため、深みぞ玉軸受への採用において、異物滞留の少ない、トルク損失の少ない深みぞ玉軸受を得ることができる。しかも、保持器は、大径端部と小径端部の径差による周速の相違によってポンプ作用を生じさせるため、通油性に優れた深みぞ玉軸受を得ることができる。   In addition, the cage assembled by combining the first divided cage and the second divided cage forms a smooth tapered outer surface and a tapered inner surface without a step, so that it is used in a deep groove ball bearing. A deep groove ball bearing with little foreign matter retention and little torque loss can be obtained. In addition, since the cage causes pumping action due to the difference in peripheral speed due to the difference in diameter between the large-diameter end and the small-diameter end, a deep groove ball bearing with excellent oil permeability can be obtained.

この発明に係る深みぞ玉軸受の実施の形態を示す縦断面図Longitudinal sectional view showing an embodiment of a deep groove ball bearing according to the present invention 図１の一部を拡大して示す断面図Sectional drawing which expands and shows a part of FIG. 第１分割保持器と第２分割保持器の結合手段の他の例を示す断面図Sectional drawing which shows the other example of the coupling | bonding means of a 1st division holder and a 2nd division holder 図１に示す保持器の側面図Side view of the cage shown in FIG. 図４に示す保持器の第１分割保持器と第２分割保持器の結合前の状態を示す側面図The side view which shows the state before the coupling | bonding of the 1st division | segmentation holder | retainer and the 2nd division | segmentation holder | retainer of the holder | retainer shown in FIG. 図４に示す保持器の一部切欠正面図FIG. 4 is a partially cutaway front view of the cage shown in FIG. この発明に係る軸受装置の実施の形態を示す概略図Schematic showing an embodiment of a bearing device according to the present invention

以下、この発明の実施の形態を図面に基づいて説明する。図１に示すように、深みぞ玉軸受Ａは、外輪１１の内径面に形成された軌道溝１２と内輪２１の外径面に設けられた軌道溝２２間にボール３１を組込み、そのボール３１を保持器４０で保持している。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, in the deep groove ball bearing A, a ball 31 is incorporated between a raceway groove 12 formed on the inner diameter surface of the outer ring 11 and a raceway groove 22 provided on the outer diameter surface of the inner ring 21. Is held by the cage 40.

外輪１１の軌道溝１２の両側に形成された一対の肩１３ａ、１３ｂのうち、軌道溝１２の一側方に位置する肩１３ａの高さは他側方に位置する肩１３ｂの高さよりも高くなっている。一方、内輪２１の軌道溝２２の両側に形成された一対の肩２３ａ、２３ｂのうち、軌道溝２２の他側方に位置する肩２３ｂの高さは一側方に位置する肩２３ａの高さより高くなっている。   Of the pair of shoulders 13a and 13b formed on both sides of the raceway groove 12 of the outer ring 11, the height of the shoulder 13a located on one side of the raceway groove 12 is higher than the height of the shoulder 13b located on the other side. It has become. On the other hand, of the pair of shoulders 23a and 23b formed on both sides of the raceway groove 22 of the inner ring 21, the height of the shoulder 23b located on the other side of the raceway groove 22 is higher than the height of the shoulder 23a located on one side. It is high.

ここで、高さの低い肩１３ｂおよび２３ａの肩の高さは、標準型深みぞ玉軸受の肩と同じ高さとされているが、標準型深みぞ玉軸受の肩の高さより低くしてもよい。   Here, the shoulder heights of the low shoulders 13b and 23a are the same as the shoulders of the standard depth groove ball bearings, but even if they are lower than the shoulder heights of the standard depth groove ball bearings. Good.

なお、説明の都合上、高さの高い肩１３ａ、２３ｂをスラスト負荷側の肩１３ａ、２３ｂといい、高さの低い肩１３ｂ、２３ａをスラスト非負荷側の肩１３ｂ、２３ａという。   For convenience of explanation, the high shoulders 13a and 23b are referred to as thrust load side shoulders 13a and 23b, and the low shoulders 13b and 23a are referred to as thrust non-load side shoulders 13b and 23a.

スラスト負荷側の肩１３ａ、２３ｂの肩高さをＨ１とし、ボール３１の球径をｄとすると、ボール３１の球径ｄに対する肩高さＨ１の比率Ｈ１／ｄは、Ｈ１／ｄ＝０．２５〜０．５０の範囲とされている。 Thrust load side of the shoulder 13a, the shoulder height of 23b as H 1, when the spherical diameter of the ball 31 is d, the ratio H 1 / d of the shoulder height H 1 relative to the spherical diameter d of the ball 31, H 1 / It is set as the range of d = 0.25-0.50.

図２、図４および図５に示すように、保持器４０は、第１分割保持器４１と、第２分割保持器４２とからなる。第１分割保持器４１はテーパ状をなし、その大径端には半円形の複数のポケット４３が周方向に等間隔に形成されている。   As shown in FIGS. 2, 4, and 5, the holder 40 includes a first divided holder 41 and a second divided holder 42. The first split holder 41 has a tapered shape, and a plurality of semicircular pockets 43 are formed at equal intervals in the circumferential direction at the large diameter end.

第２分割保持器４２も第１分割保持器４１と同様にテーパ状をなし、そのテーパ角度は第１分割保持器４１のテーパ角度と同一とされ、その小径端面の外径および内径は、第１分割保持器４１の大径端面の外径および内径と同径とされている。   Similarly to the first divided holder 41, the second divided holder 42 also has a tapered shape, the taper angle of which is the same as the taper angle of the first divided holder 41, and the outer diameter and inner diameter of the small-diameter end face are The outer diameter and inner diameter of the large-diameter end face of the one-part cage 41 are the same.

また、第２分割保持器４２の小径端には、第１分割保持器４１に形成されたポケット４３と同数の半円形のポケット４４が周方向に等間隔に形成され、その複数のポケット４４は、第１分割保持器４１の大径端面に第２分割保持器４２の小径端面を衝合させる接続状態でボール収容用の円形のポケット４５を形成するようになっている。   In addition, the same number of semicircular pockets 44 as the pockets 43 formed in the first split holder 41 are formed at equal intervals in the circumferential direction at the small-diameter end of the second split holder 42. A circular pocket 45 for accommodating a ball is formed in a connected state in which the small-diameter end face of the second split holder 42 is brought into contact with the large-diameter end face of the first split holder 41.

図２、図５および図６に示すように、第１分割保持器４１の隣接するポケット４３間に形成された柱部４６の端面外周部には、第２分割保持器４２に向けて鈎部４７ａを先端に有する係合爪４７が形成され、一方、第２分割保持器４２の隣接するポケット４４間に形成された柱部４８の外周には上記係合爪４７が係合可能な係合凹部４９が設けられ、その係合凹部４９に対する係合爪４７の係合によって第１分割保持器４１と第２分割保持器４２とは軸方向に結合されて、軸方向に非分離とされる。   As shown in FIGS. 2, 5, and 6, an end surface outer peripheral portion of the column portion 46 formed between the adjacent pockets 43 of the first divided holder 41 has a flange portion toward the second divided holder 42. An engaging claw 47 having a tip 47a is formed. On the other hand, the outer periphery of the column portion 48 formed between the adjacent pockets 44 of the second divided holder 42 is engageable with the engaging claw 47. A concave portion 49 is provided, and the first split holder 41 and the second split holder 42 are coupled in the axial direction by the engagement of the engaging claw 47 with the engaging concave portion 49 and are not separated in the axial direction. .

ここで、図２では、第１分割保持器４１の柱部４６の端面外周部に係合爪４７を形成し、第２分割保持器４２の柱部４８の外周に係合凹部４９を設けたが、図３に示すように、第１分割保持器４１の柱部４６の端面内周部に係合爪４７を形成し、第２分割保持器４２の柱部４８の内周に係合凹部４９を設けるようにしてもよい。また、図では省略したが、第２分割保持器４２の柱部４８端面に係合爪を設け、第１分割保持器４１の柱部４６に係合凹部を設けるようにしてもよい。   Here, in FIG. 2, the engaging claw 47 is formed on the outer peripheral portion of the end surface of the column portion 46 of the first divided holder 41, and the engaging recess 49 is provided on the outer periphery of the column portion 48 of the second divided holder 42. However, as shown in FIG. 3, the engagement claw 47 is formed on the inner peripheral portion of the end surface of the column portion 46 of the first divided holder 41, and the engagement recess is formed on the inner periphery of the column portion 48 of the second divided holder 42. 49 may be provided. Although omitted in the drawing, an engaging claw may be provided on the end face of the column part 48 of the second divided holder 42, and an engaging recess may be provided in the column part 46 of the first divided holder 41.

図３に示すように、第１分割保持器４１の柱部４６の端面内周部に係合爪４７を形成する場合は、係合爪４７の先端部に上向きに鈎部４７ａを設けるようにする。   As shown in FIG. 3, when the engagement claw 47 is formed on the inner peripheral portion of the end surface of the column portion 46 of the first divided holder 41, the flange portion 47 a is provided upward at the distal end portion of the engagement claw 47. To do.

第１分割保持器４１および第２分割保持器４２のそれぞれは、合成樹脂の成形品とされている。この場合、保持器４０は、深みぞ玉軸受を潤滑する潤滑オイルに曝されるため、耐油性に優れた合成樹脂を用いるようにする。   Each of the first split holder 41 and the second split holder 42 is a molded product of synthetic resin. In this case, since the cage 40 is exposed to the lubricating oil that lubricates the deep groove ball bearing, a synthetic resin excellent in oil resistance is used.

そのような樹脂として、ポリアミド４６（ＰＡ４６）、ポリアミド６６（ＰＡ６６）、ポリアミド９Ｔ(ＰＡ９Ｔ)、ポリエーテルエーテルケトン樹脂(ＰＥＥＫ)、ポリフェニレンサルファイド樹脂(ＰＰＳ)を挙げることができる。これらの樹脂は、潤滑オイルの種類に応じて適切なものを選択して使用すればよい。   Examples of such resins include polyamide 46 (PA46), polyamide 66 (PA66), polyamide 9T (PA9T), polyetheretherketone resin (PEEK), and polyphenylene sulfide resin (PPS). These resins may be selected and used according to the type of lubricating oil.

実施の形態で示す深みぞ玉軸受は上記の構造からなり、その深みぞ玉軸受の組立てに際しては、外輪１１の内側に内輪２１を挿入し、その内輪２１の軌道溝２２と外輪１１の軌道溝１２間に所要数のボール３１を組込む。   The deep groove ball bearing shown in the embodiment has the above-described structure. When the deep groove ball bearing is assembled, the inner ring 21 is inserted inside the outer ring 11, and the race groove 22 of the inner ring 21 and the race groove of the outer ring 11 are inserted. A required number of balls 31 are assembled between 12.

このとき、内輪２１を外輪１１に対して径方向にオフセットして、内輪２１の外径面の一部を外輪１１の内径面の一部に当接して、その当接部位から周方向に１８０度ずれた位置に三日月形の空間を形成し、その空間の一側方から内部にボール３１を組込むようにする。   At this time, the inner ring 21 is offset in the radial direction with respect to the outer ring 11, a part of the outer diameter surface of the inner ring 21 is brought into contact with a part of the inner diameter surface of the outer ring 11, and 180 degrees in the circumferential direction from the contact part. A crescent-shaped space is formed at a position deviated, and the ball 31 is assembled from one side of the space.

そのボール３１の組込みに際して、外輪１１のスラスト負荷側の肩１３ａや内輪２１のスラスト負荷側の肩２３ｂの肩高さＨ１が必要以上に高い場合には、ボール３１の組込みを阻害することになるが、実施の形態では、ボール３１の球径ｄに対する肩高さＨ１の比率Ｈ１／ｄが、０．５０を超えることのない高さとされているため、外輪１１と内輪２１間にボール３１を確実に組込むことができる。 Upon incorporation of the balls 31, when the shoulder height H 1 of the thrust load side of the shoulder 23b of the thrust load side of the shoulder 13a and the inner ring 21 of the outer ring 11 is higher than necessary, to inhibit the incorporation of the balls 31 However, in the embodiment, since the ratio H 1 / d of the shoulder height H 1 to the ball diameter d of the ball 31 does not exceed 0.50, the gap between the outer ring 11 and the inner ring 21 is The ball 31 can be reliably assembled.

ボール３１の組込み後、内輪２１の中心を外輪１１の中心に一致させてボール３１を周方向に等間隔に配置し、外輪１１と内輪２１の対向部間に第１分割保持器４１と第２分割保持器４２を挿入する。   After the ball 31 is assembled, the center of the inner ring 21 is made to coincide with the center of the outer ring 11, the balls 31 are arranged at equal intervals in the circumferential direction, and the first split cage 41 and the second ring are disposed between the opposing portions of the outer ring 11 and the inner ring 21. The division holder 42 is inserted.

このとき、第１分割保持器４１は、外輪１１の高さの高い肩１３ａ側からポケット４３を先にして外輪１１と内輪２１の対向部間に挿入し、一方、第２分割保持器４２は、外輪１１の高さの低い肩１３ｂ側からポケット４４を先にして外輪１１と内輪２１の対向部間に挿入する。   At this time, the first split cage 41 is inserted between the opposing portions of the outer ring 11 and the inner ring 21 with the pocket 43 first from the shoulder 13a side where the height of the outer ring 11 is high, while the second split cage 42 is The outer ring 11 is inserted between the opposed portions of the outer ring 11 and the inner ring 21 with the pocket 44 first from the lower shoulder 13b side.

第１分割保持器４１および第２分割保持器４２の挿入後、第１分割保持器４１に形成された係合爪４７が第２分割保持器４２に設けられた係合凹部４９に軸方向で対向し、かつ、半円形ポケット４３、４４がボール３１と軸方向で対向するよう、第１分割保持器４１および第２分割保持器４２の向きを調整して、その第１分割保持器４１および第２分割保持器４２を軸方向に押し込むようにする。   After the insertion of the first split holder 41 and the second split holder 42, the engaging claws 47 formed in the first split holder 41 are axially inserted into the engaging recesses 49 provided in the second split holder 42. The first divided holder 41 and the second divided holder 42 are adjusted so that the semicircular pockets 43 and 44 are opposed to each other in the axial direction so that the semicircular pockets 43 and 44 are opposed to each other in the axial direction. The second split cage 42 is pushed in the axial direction.

上記のように、第１分割保持器４１および第２分割保持器４２の向きを調整して、双方の分割保持器４１、４２を軸方向に押し込むことにより、図２に示すように、係合爪４７が係合凹部４９に係合し、第１分割保持器４１と第２分割保持器４２が互いに結合されて保持器４０が形成され、複数のボール３１は円形に組み合わされたポケット４５のそれぞれで保持されて、深みぞ玉軸受Ａが組立状態とされる。   As described above, by adjusting the orientation of the first divided holder 41 and the second divided holder 42 and pushing both the divided holders 41 and 42 in the axial direction, as shown in FIG. The claw 47 engages with the engaging recess 49, and the first divided holder 41 and the second divided holder 42 are coupled to each other to form the holder 40, and the plurality of balls 31 are formed in the circularly combined pocket 45. The deep groove ball bearings A are held in the assembled state.

ここで、ボール３１を保持する保持器４０は、テーパ角度を同一とするテーパ状第１分割保持器４１とテーパ状第２分割保持器４２とからなり、その第１分割保持器４１の大径端面の外径および内径は、その大径端面に衝合される第２分割保持器４２の小径端面の外径および内径と同径であるため、第１分割保持器と第２分割保持器の結合によって組み立てられた保持器４０の外表面および内表面は、段差のない滑らかなテーパ面を形成することになる。   Here, the retainer 40 that holds the ball 31 includes a tapered first split retainer 41 and a tapered second split retainer 42 having the same taper angle, and the first split retainer 41 has a large diameter. Since the outer diameter and inner diameter of the end surface are the same as the outer diameter and inner diameter of the small-diameter end surface of the second split retainer 42 abutted on the large-diameter end surface, the first split retainer and the second split retainer The outer surface and the inner surface of the cage 40 assembled by bonding form a smooth tapered surface without a step.

このため、上記保持器４０の深みぞ玉軸受への採用において、異物滞留の少ない深みぞ玉軸受Ａを得ることができる。また、潤滑オイルの撹拌抵抗も小さく、トルク損失の少ない玉軸受Ａを得ることができる。   For this reason, in the adoption of the cage 40 in a deep groove ball bearing, a deep groove ball bearing A with less foreign matter retention can be obtained. Further, it is possible to obtain a ball bearing A with a small stirring resistance of the lubricating oil and a small torque loss.

さらに、保持器４０はテーパ状であるため、回転時、大径端部と小径端部の径の相違によって周速が相違し、軸受内部にポンプ作用が生じる。そのポンプ作用によって、潤滑オイルが軸受内に強制的に送り込まれることになり、通油性の良好な深みぞ玉軸受Ａを得ることができる。   Furthermore, since the retainer 40 is tapered, the peripheral speed differs depending on the difference in diameter between the large-diameter end and the small-diameter end during rotation, and a pumping action is generated inside the bearing. Due to the pumping action, the lubricating oil is forcibly fed into the bearing, and the deep groove ball bearing A having good oil permeability can be obtained.

図７は、実施の形態で示す深みぞ玉軸受Ａを用いて従動側のヘリカルギヤ５０を支持するシャフト５１を回転自在に支持した軸受装置を示す。この場合、深みぞ玉軸受Ａは、内輪２１のスラスト負荷側の肩２３ｂがヘリカルギヤ５０側に位置する組付けとする。また、深みぞ玉軸受Ａは、一部が油浴に浸かる組付けとする。   FIG. 7 shows a bearing device that rotatably supports a shaft 51 that supports the helical gear 50 on the driven side using the deep groove ball bearing A shown in the embodiment. In this case, the deep groove ball bearing A is assembled so that the shoulder 23b on the thrust load side of the inner ring 21 is located on the helical gear 50 side. The deep groove ball bearing A is assembled so that a part thereof is immersed in an oil bath.

上記軸受装置において、駆動側ヘリカルギヤ５２から従動側ヘリカルギヤ５０に回転を伝達すると、シャフト５１にスラスト力が負荷され、そのスラスト力は深みぞ玉軸受Ａにおける内輪２１のスラスト負荷側の肩２３ｂと外輪１１のスラスト負荷側の肩１３ａで支持される。   In the bearing device, when the rotation is transmitted from the drive side helical gear 52 to the driven side helical gear 50, a thrust force is applied to the shaft 51, and the thrust force is a thrust load side shoulder 23b of the inner ring 21 and the outer ring in the deep groove ball bearing A. 11 on the thrust load side shoulder 13a.

このとき、ボール３１にもスラスト力が負荷され、内輪２１のスラスト負荷側の肩２３ｂと外輪１１のスラスト負荷側の肩１３ａが必要以上に低い場合、ボール３１が肩１３ａ、２３ｂに乗り上がり、肩１３ａ、２３ｂのエッジを損傷させる可能性がある。   At this time, a thrust force is also applied to the ball 31, and when the thrust load side shoulder 23b of the inner ring 21 and the thrust load side shoulder 13a of the outer ring 11 are lower than necessary, the ball 31 rides on the shoulders 13a, 23b, There is a possibility of damaging the edges of the shoulders 13a and 23b.

実施の形態では、ボール３１の球径ｄに対する肩高さＨ１の比率Ｈ１／ｄを０．２５以上としているため、ボール３１の乗り上げを確実に阻止することができる。 In the embodiment, since the ratio H 1 / d of the shoulder height H 1 to the ball diameter d of the ball 31 is set to 0.25 or more, the riding of the ball 31 can be reliably prevented.

１１ 外輪
１２ 軌道溝
１３ａ 肩
１３ｂ 肩
２１ 内輪
２２ 軌道溝
２３ａ 肩
２３ｂ 肩
３１ ボール
４０ 保持器
４１ 第１分割保持器
４２ 第２分割保持器
４３ 半円形ポケット
４４ 半円形ポケット
４５ 円形ポケット
４６ 柱部
４７ 係合爪
４７ａ 鈎部
４８ 柱部
４９ 係合凹部
５０ ヘリカルギヤ
５１ シャフト 11 Outer ring 12 Track groove 13a Shoulder 13b Shoulder 21 Inner ring 22 Track groove 23a Shoulder 23b Shoulder 31 Ball 40 Holder 41 First divided holder 42 Second divided holder 43 Semicircular pocket 44 Semicircular pocket 45 Circular pocket 46 Column 47 Engaging claw 47a collar 48 column 49 engaging recess 50 helical gear 51 shaft

Claims (8)

テーパ状とされた第１分割保持器と、その第１分割保持器とテーパ角度が同じとされて、小径端面の外径および内径が第１分割保持器の大径端面の外径および内径と同径とされたテーパ状の第２分割保持器とからなり、前記第１分割保持器の大径端と第２分割保持器の小径端のそれぞれに、第１分割保持器の大径端面に第２分割保持器の小径端面を衝合させる接続状態でボール収容用の円形のポケットを形成する複数の半円形ポケットを周方向に等間隔に設け、前記第１分割保持器の半円形ポケット間に形成された柱部の端面と第２分割保持器の半円形ポケット間に形成された柱部の端面の、一方の端面の外周部または内周部に、先端が鈎部とされた係合爪を設け、他方の端面に、その係合爪が係合可能とされ、係合状態で第１分割保持器と第２分割保持器とを軸方向に結合する係合凹部を設けたことを特徴とする深みぞ玉軸受用保持器。   The tapered first split cage has the same taper angle as that of the first split cage, and the outer diameter and inner diameter of the small diameter end surface are the outer diameter and inner diameter of the large diameter end surface of the first split cage. A tapered second split cage having the same diameter, and a large diameter end surface of the first split cage on each of the large diameter end of the first split cage and the small diameter end of the second split cage. A plurality of semicircular pockets forming circular pockets for accommodating balls in a connected state where the small-diameter end faces of the second split cage are abutted are provided at equal intervals in the circumferential direction, and between the semicircular pockets of the first split cage Engagement of the end surface of the column portion formed on the outer peripheral portion or inner peripheral portion of one end surface between the end surface of the column portion and the end surface of the column portion formed between the semicircular pockets of the second split cage. A claw is provided, and the engaging claw can be engaged with the other end surface. 2 split cage and deep groove cage for a ball bearing, characterized in that a engaging recess that binds axially. 前記第１分割保持器および第２分割保持器のそれぞれが、合成樹脂の成形品からなる請求項１に記載の深みぞ玉軸受用保持器。   The deep groove ball bearing cage according to claim 1, wherein each of the first divided cage and the second divided cage is made of a synthetic resin molded product. 前記合成樹脂が、ポリアミド樹脂からなる請求項２に記載の深みぞ玉軸受用保持器。   The cage for deep groove ball bearings according to claim 2, wherein the synthetic resin is made of a polyamide resin. 前記ポリアミド樹脂が、ポリアミド４６、ポリアミド６６、ポリアミド９Ｔのうちの一種からなる請求項３に記載の深みぞ玉軸受用保持器。   The cage for deep groove ball bearings according to claim 3, wherein the polyamide resin is one of polyamide 46, polyamide 66, and polyamide 9T. 前記合成樹脂が、ポリエーテルエーテルケトン樹脂からなる請求項２に記載の深みぞ玉軸受用保持器。   The cage for deep groove ball bearings according to claim 2, wherein the synthetic resin is a polyether ether ketone resin. 前記合成樹脂が、ポリフェニレンサルファイド樹脂からなる請求項２に記載の深みぞ玉軸受用保持器。   The cage for deep groove ball bearings according to claim 2, wherein the synthetic resin is made of polyphenylene sulfide resin. 内径面に軌道溝が形成された外輪と、外径面に軌道溝が形成された内輪と、外輪の軌道溝と内輪の軌道溝間に組込まれたボールと、そのボールを保持する保持器とからなり、前記外輪軌道溝の一側の肩と内輪軌道溝の他側の肩の少なくとも一方の高さを、外輪軌道溝の他側の肩または内輪軌道溝の一側の肩の高さより高くし、その高さの高い肩の肩高さをＨ１、ボールの球径をｄとしたとき、ボールの球径ｄに対する肩高さＨ１の比率Ｈ１／ｄを０．２５〜０．５０の範囲とした深みぞ玉軸受において、
前記保持器が請求項１乃至６のいずれかの項に記載の深みぞ玉軸受用保持器かなることを特徴とする深みぞ玉軸受。 An outer ring having a raceway groove formed on the inner diameter surface, an inner ring having a raceway groove formed on the outer diameter surface, a ball assembled between the raceway groove of the outer ring and the raceway groove of the inner ring, and a cage for holding the ball The height of at least one of the shoulder on one side of the outer ring raceway groove and the shoulder on the other side of the inner ring raceway groove is higher than the height of the shoulder on the other side of the outer ring raceway groove or one side of the inner ring raceway groove. The ratio H 1 / d of the shoulder height H 1 with respect to the ball diameter d is 0.25 to 0. 0, where H 1 is the shoulder height of the high shoulder and d is the ball diameter of the ball. In deep groove ball bearings with a range of 50,
A deep groove ball bearing, wherein the retainer is a deep groove ball bearing retainer according to any one of claims 1 to 6. ヘリカルギヤが設けられたシャフトを油浴に一部が浸かる一対の転がり軸受で回転自在に支持した軸受装置において、
前記一対の転がり軸受が、請求項７に記載の深みぞ玉軸受からなることを特徴とする軸受装置。 In a bearing device in which a shaft provided with a helical gear is rotatably supported by a pair of rolling bearings partially immersed in an oil bath,
The bearing device characterized in that the pair of rolling bearings comprises the deep groove ball bearing according to claim 7.
JP2011236051A 2011-10-27 2011-10-27 Retainer for deep groove ball bearing, deep groove ball bearing using the retainer, and bearing device Pending JP2013092242A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105020263A (en) * 2014-04-28 2015-11-04 宁波市鄞州金鑫轴承五金有限公司 Bearing
CN106989103A (en) * 2015-10-20 2017-07-28 斯凯孚公司 Two-part retainer
KR20180002229U (en) * 2017-01-12 2018-07-20 쑤-잉 리 Positive linear motion apparatus

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105020263A (en) * 2014-04-28 2015-11-04 宁波市鄞州金鑫轴承五金有限公司 Bearing
CN106989103A (en) * 2015-10-20 2017-07-28 斯凯孚公司 Two-part retainer
KR20180002229U (en) * 2017-01-12 2018-07-20 쑤-잉 리 Positive linear motion apparatus

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