JP6050000B2 - Deep groove ball bearing and bearing device - Google Patents

Deep groove ball bearing and bearing device Download PDF

Info

Publication number
JP6050000B2
JP6050000B2 JP2012006915A JP2012006915A JP6050000B2 JP 6050000 B2 JP6050000 B2 JP 6050000B2 JP 2012006915 A JP2012006915 A JP 2012006915A JP 2012006915 A JP2012006915 A JP 2012006915A JP 6050000 B2 JP6050000 B2 JP 6050000B2
Authority
JP
Japan
Prior art keywords
raceway
shoulder
bearing
ball
deep groove
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Fee Related
Application number
JP2012006915A
Other languages
Japanese (ja)
Other versions
JP2013148115A (en
Inventor
克明 佐々木
克明 佐々木
朋久 魚住
朋久 魚住
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
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 Corp filed Critical NTN Corp
Priority to JP2012006915A priority Critical patent/JP6050000B2/en
Publication of JP2013148115A publication Critical patent/JP2013148115A/en
Application granted granted Critical
Publication of JP6050000B2 publication Critical patent/JP6050000B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—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
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • 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
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Description

この発明は、深みぞ玉軸受およびその深みぞ玉軸受を用いた軸受装置に関する。   The present invention relates to a deep groove ball bearing and a bearing device using the deep groove ball bearing.

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、回転トルクが大きく、燃料の消費量が多くなるという問題が生じる。その省燃費化を図るため、回転トルクの小さ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 rotational torque is large and the amount of fuel consumption increases. In order to save fuel consumption, there are many cases in which deep groove ball bearings having a small rotational 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して、大きなスラスト荷重を受けることができるようにしている。   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, to suppress a decrease in the durability of the bearing, and to receive a large thrust load.

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、大きなスラスト荷重を受けることができるものの、開放型の軸受であるため、トランスミッションに採用した場合に、次のような不都合が生じる。すなわち、軸受は、ミッションケース内の貯留オイルによって潤滑され、その潤滑オイルにはギヤ摩耗粉等の異物が混入しているため、潤滑オイルと共に異物が軸受内部に侵入し、その異物の噛み込みによって転動面や転走面が損傷し、軸受寿命を低下させることになる。   By the way, although the deep groove ball bearing described in Patent Document 1 can receive a large thrust load, since it is an open type bearing, the following inconvenience occurs when it is used in a transmission. In other words, the bearing is lubricated by the oil stored in the transmission case, and foreign matter such as gear wear powder is mixed in the lubricating oil. The rolling surfaces and rolling surfaces are damaged, and the bearing life is shortened.

上記のような不都合は、シール部材の組込みによって軸受空間を密閉することにより解消することができるが、回転側の軌道輪はシール部材が弾性接触する状態で回転するため、回転抵抗が大きく、トルク損失が多くなるという問題が発生する。   The inconveniences as described above can be solved by sealing the bearing space by incorporating the seal member. However, since the rotating ring rotates in a state where the seal member is in elastic contact with the seal member, the rotation resistance is large and the torque is increased. The problem of increased loss occurs.

この発明の課題は、トルク損失を増大させることなく異物の侵入を防止することができるようにしたスラスト負荷容量の大きな深みぞ玉軸受および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 and a bearing device having a large thrust load capacity capable of preventing the intrusion of foreign matters without increasing torque loss.

上記の課題を解決するために、この発明に係る深みぞ玉軸受においては、内径面に軌道溝を有する外方軌道輪と、外径面に軌道溝を有する内方軌道輪と、外方軌道輪の軌道溝と内方軌道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、前記外方軌道輪における軌道溝の一側の肩と前記内方軌道輪における軌道溝の他側の肩の少なくとも一方の肩の高さを、外方軌道輪の他側の肩と前記内方軌道輪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、前記外方軌道輪と内方軌道輪の一方が固定側とされ、他方が回転側として使用される深みぞ玉軸受において、前記外方軌道輪と前記内方軌道輪の対向面間に形成された軸受空間の両端開口部内にシール部材を組込んで固定側の軌道輪で支持し、そのシール部材には回転側の軌道輪に弾性接触して軸受空間の両端開口を密閉するシールリップを設け、そのシールリップの少なくとも先端部を、回転側の軌道輪との接触により摩耗して非接触となるか、または、接触圧が零とみなせる程度の軽接触となる高摩耗材で形成した構成を採用したのである。 In order to solve the above problems, in the deep groove ball bearing according to the present invention, an outer race ring having a raceway groove on an inner diameter surface, an inner race ring having a raceway groove on an outer diameter surface, and an outer raceway A ball assembled between the raceway groove of the ring and the raceway groove of the inner raceway, and a cage for holding the ball, and a shoulder on one side of the raceway groove in the outer raceway and the inner raceway The height of at least one of the shoulders on the other side of the raceway groove is higher than the height of the shoulder on the other side of the outer raceway and the shoulder on one side of the inner raceway, and the shoulder with the higher height When the shoulder height of H1 is H1 and the ball sphere diameter is d, the ratio H1 / d of the shoulder height H1 to the ball sphere diameter d is in the range of 0.25 to 0.50. In a deep groove ball bearing in which one of the inner races is a fixed side and the other is used as a rotation side, the outer race and the outer race A seal member is incorporated in the opening at both ends of the bearing space formed between the opposing surfaces of the side raceway ring and supported by the fixed side raceway ring. A seal lip that seals the opening at both ends is provided, and at least the tip of the seal lip is worn out by contact with the raceway on the rotating side and becomes non-contact, or a light contact that can be regarded as zero contact pressure The construction made of high wear material is adopted.

ここで、高摩耗材とは、オイル潤滑下において、４０００ｒｐｍの回転速度でもって軸受を回転させた場合に、回転開始から６０分以内のならし運転程度で摩耗するものをいい、ゴムであってもよく、あるいは、合成樹脂であってもよい。   Here, the high wear material refers to a material that wears within about 60 minutes from the start of rotation when the bearing is rotated at a rotational speed of 4000 rpm under oil lubrication, and is rubber. Alternatively, it may be a synthetic resin.

この発明に係る深みぞ玉軸受において、シールリップは、回転側軌道輪の周面に形成されたシール溝の内壁面に弾性接触するアキシャル接触とされたものであってもよく、あるいは、回転側軌道輪の円筒状周面に弾性接触するラジアル接触とされたものであってもよい。   In the deep groove ball bearing according to the present invention, the seal lip may be an axial contact that elastically contacts the inner wall surface of the seal groove formed on the peripheral surface of the rotating raceway, or the rotating lip It may be a radial contact that elastically contacts the cylindrical peripheral surface of the raceway.

上記のように、シールリップの少なくとも先端部を高摩耗材で形成することにより、運転初期に接触タイプであったシールリップが、回転側軌道輪との接触により早期に摩耗して、内輪との間に微細なラビリンス隙間を形成する非接触の状態または接触圧が零と見なせる程度の軽接触の状態となり、トルク損失を低減する状態で異物の侵入を防止することができる。   As described above, by forming at least the tip of the seal lip with a high wear material, the seal lip, which was a contact type in the initial stage of operation, wears out early due to contact with the rotating raceway, A non-contact state in which a fine labyrinth gap is formed between them or a light contact state where the contact pressure can be regarded as zero can be achieved, and foreign matter can be prevented from entering in a state where torque loss is reduced.

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においては、上記のように、シール部材の組込みによって軸受内部への異物の侵入を防止することができ、そのシール部材に形成されたシールリップは回転側軌道輪との接触により早期に摩耗して、微細なラビリンス隙間を形成する非接触の状態または接触圧が零と見なせる程度の軽接触の状態となるため、トルク損失を増大させることなく異物の侵入を防止することができ、スラスト負荷容量の大きな深みぞ玉軸受の耐久性の低下を抑制することができる。   In the deep groove ball bearing according to the present invention, as described above, it is possible to prevent foreign matter from entering the bearing by incorporating the seal member, and the seal lip formed on the seal member can be Wears out early due to contact, resulting in a non-contact state that forms a fine labyrinth gap or a light contact state where contact pressure can be regarded as zero, thus preventing intrusion of foreign matter without increasing torque loss It is possible to suppress a decrease in durability of the deep groove ball bearing having a large thrust load capacity.

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. 図２示すシールリップの摩耗状態を示す断面図Sectional drawing which shows the abrasion state of the seal lip shown in FIG. この発明に係る深みぞ玉軸受の他の実施の形態を示す縦断面図Longitudinal sectional view showing another embodiment of a deep groove ball bearing according to the present invention 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、外方軌道輪としての外輪１１と、内方軌道輪としての内輪２１と、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間に組み込まれたボール３１と、そのボール３１を保持する保持器４０とを有している。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, the deep groove ball bearing A includes an outer ring 11 as an outer race ring, an inner ring 21 as an inner race ring, a raceway groove 12 formed on an inner diameter surface of the outer ring 11, and an inner ring 21. It has the ball | bowl 31 integrated between the track grooves 22 provided in the outer-diameter surface, and the holder | retainer 40 holding the ball | bowl 31. FIG.

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.

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および第２分割保持器４２のそれぞれは、複数の半球状のポケット部４３と平板状の結合板部４４とを周方向に交互に設けた波形分割保持器からなり、第１分割保持器４１の外径は第２分割保持器４２の外径より小径とされている。   The holder 40 includes a first divided holder 41 and a second divided holder 42. Each of the first divided holder 41 and the second divided holder 42 is composed of a waveform divided holder in which a plurality of hemispherical pocket portions 43 and flat coupling plate portions 44 are alternately provided in the circumferential direction. The outer diameter of the one split cage 41 is smaller than the outer diameter of the second split cage 42.

また、第１分割保持器４１は、外輪１１の高さの高い肩１３ａから軸受内部に挿入可能とされている。一方、第２分割保持器４２は、外輪１１の高さの低い肩１３ｂから軸受内部に挿入可能とされている。   Moreover, the 1st division | segmentation holder | retainer 41 can be inserted in a bearing inside from the shoulder 13a with the high height of the outer ring | wheel 11. FIG. On the other hand, the second split cage 42 can be inserted into the bearing through the shoulder 13b having a low height of the outer ring 11.

第１分割保持器４１と第２分割保持器４２は、半球状ポケット部４３が軸方向で対向して球状のポケットを形成する組み合わせとされ、互いに衝合する結合板部４４を貫通するリベット４５の端部の加締めによって互いに結合されている。   The first split holder 41 and the second split holder 42 are a combination in which the hemispherical pocket portions 43 are opposed to each other in the axial direction to form a spherical pocket, and a rivet 45 that penetrates the coupling plate portion 44 that abuts each other. Are joined to each other by caulking the ends of the two.

外輪１１と内輪２１の対向面間に形成された軸受空間の両端の開口部内にはシール部材５０が組み込まれている。シール部材５０は、弾性部材からなり、芯金５１により補強されている。   Seal members 50 are incorporated in openings at both ends of the bearing space formed between the opposing surfaces of the outer ring 11 and the inner ring 21. The seal member 50 is made of an elastic member and is reinforced by a cored bar 51.

図２に示すように、シール部材５０は、固定輪としての外輪１１の肩内径面に形成されたシール取付溝１４内に外周部が嵌合されて外輪１１により支持されている。シール部材５０の内周部には、内向きのシールリップ５２と外向きのシールリップ５３が設けられ、内向きシールリップ５２の先端部は、内輪２１の肩外径面に形成されたシール溝２４の内壁面２５にアキシャル接触し、一方、外向きシールリップ５３の先端部は、シール溝２４の軸方向外方に形成された円筒面２６にラジアル接触して、軸受空間を密閉している。   As shown in FIG. 2, the seal member 50 is supported by the outer ring 11 with an outer peripheral portion fitted in a seal mounting groove 14 formed on the shoulder inner diameter surface of the outer ring 11 as a fixed ring. An inward seal lip 52 and an outward seal lip 53 are provided on the inner peripheral portion of the seal member 50, and the tip of the inward seal lip 52 is a seal groove formed on the shoulder outer diameter surface of the inner ring 21. 24, the tip of the outward seal lip 53 is in radial contact with the cylindrical surface 26 formed axially outward of the seal groove 24 to seal the bearing space. .

シールリップ５２、５３のそれぞれは、回転側の内輪２１との接触により早期に摩耗する高摩耗材で形成されている。   Each of the seal lips 52, 53 is formed of a high wear material that wears quickly due to contact with the inner ring 21 on the rotating side.

ここで、高摩耗材とは、深みぞ玉軸受Ａを、鉱油系オイルによるオイル潤滑状態において、回転速度；４０００ｒｐｍ、軸受温度；３０℃、回転トルク；０．０７５Ｎ・ｍの運転条件下で回転させ、その回転開始から６０分以内のならし運転程度で摩耗して、内輪２１に対して非接触となるか、または、接触圧が零とみなせる程度の軽接触となる材料をいい、ゴムからなるものであってもよく、合成樹脂からなるものであってもよい。   Here, the high wear material means that the deep groove ball bearing A is rotated under an operating condition of a rotational speed: 4000 rpm, a bearing temperature: 30 ° C., a rotational torque: 0.075 N · m in an oil lubrication state with mineral oil. It is a material that wears in the run-in period of 60 minutes or less from the start of rotation and is not in contact with the inner ring 21, or a light contact with which the contact pressure can be regarded as zero. It may be made of synthetic resin.

図２では、シールリップ５２、５３の全体を高摩耗材で形成しているが、先端部のみを高摩耗材で形成するようにしてもよい。   In FIG. 2, the entire seal lips 52 and 53 are formed of a high wear material, but only the tip portion may be formed of a high wear material.

実施の形態で示す深みぞ玉軸受のように、軸受空間の開口部内にシール部材５０を組込み、そのシール部材５０の内周に形成された内向きシールリップ５２の先端部をシール溝２４の内壁面２５に弾性接触させ、外向きシールリップ５３をシール溝２４の軸方向外方に形成された円筒状周面としての円筒面２６に弾性接触させて、軸受空間の開口部を密閉することにより、そのシール部材５０によって潤滑オイルに混入するギヤ摩耗粉等の異物が軸受内部に侵入するのを防止することができる。   Like the deep groove ball bearing shown in the embodiment, the seal member 50 is incorporated in the opening of the bearing space, and the tip of the inward seal lip 52 formed on the inner periphery of the seal member 50 is inserted into the seal groove 24. By elastically contacting the wall surface 25, the outward seal lip 53 is elastically contacted with a cylindrical surface 26 as a cylindrical peripheral surface formed outwardly in the axial direction of the seal groove 24 to seal the opening of the bearing space. The seal member 50 can prevent foreign matters such as gear wear powder mixed in the lubricating oil from entering the bearing.

ここで、シールリップ５２、５３が内輪２１と常に弾性接触する状態にあると、その接触抵抗が回転抵抗となってトルク損失が生じることになる。しかし、実施の形態においては、シールリップ５２、５３のそれぞれを高摩耗材により形成しているため、運転初期に接触タイプであったシールリップ５２、５３の先端部は、内輪２１との接触により早期に摩耗することになる。図３は、シールリップ５２、５３が摩耗して、シール溝２４の内壁面２５との間、および円筒面２６との間で微細なラビリンス隙間５５を形成する非接触の状態を示しているが、接触圧が零と見なせる程度の軽接触の状態となる場合もある。   Here, if the seal lips 52 and 53 are always in elastic contact with the inner ring 21, the contact resistance becomes rotational resistance and torque loss occurs. However, in the embodiment, since each of the seal lips 52 and 53 is made of a high wear material, the front ends of the seal lips 52 and 53 that were contact types in the initial operation are brought into contact with the inner ring 21. It will wear out early. FIG. 3 shows a non-contact state in which the seal lips 52 and 53 are worn and a fine labyrinth gap 55 is formed between the inner wall surface 25 of the seal groove 24 and the cylindrical surface 26. In some cases, the contact pressure is light enough that the contact pressure can be regarded as zero.

このように、シールリップ５２、５３は、運転初期に早期に摩耗して非接触の状態となり、あるいは、接触圧が零と見なせる程度の軽接触の状態となるため、トルク損失を低減する状態で異物の侵入を防止することができ、異物の噛み込みによる損傷の発生を防止し、大きなスラスト力を受けることができる深みぞ玉軸受の寿命の低下を抑制することができる。   As described above, the seal lips 52 and 53 are worn out early in the initial stage of operation and are in a non-contact state, or in a light contact state in which the contact pressure can be regarded as zero, so that torque loss is reduced. Intrusion of foreign matter can be prevented, occurrence of damage due to biting of foreign matter can be prevented, and a decrease in the life of a deep groove ball bearing that can receive a large thrust force can be suppressed.

図２では、シール部材５０の内周に形成された内向きシールリップ５２をシール溝２４の内壁面２５にアキシャル接触させるようにしたが、図４に示すように、内向きシールリップ５２および外向きシールリップ５３のそれぞれ先端部を内輪２１の円筒状周面としての肩外径面２７に弾性接触させるようにしてもよい。   In FIG. 2, the inward seal lip 52 formed on the inner periphery of the seal member 50 is in axial contact with the inner wall surface 25 of the seal groove 24. However, as shown in FIG. You may make it each elastically contact the front-end | tip part of the direction seal lip 53 with the shoulder outer-diameter surface 27 as a cylindrical surrounding surface of the inner ring | wheel 21. FIG.

図５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６０を支持するシャフト６１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６０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. 5 shows a bearing device that rotatably supports a shaft 61 that supports the helical gear 60 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 60 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６２から従動側ヘリカルギヤ６０に回転を伝達すると、シャフト６１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 driving side helical gear 62 to the driven side helical gear 60, a thrust force is applied to the shaft 61, and the thrust force is applied to the thrust load side shoulder 23b of the inner ring 21 in the deep groove ball bearing A and the outer ring. 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.

実施の形態では、深みぞ玉軸受が内輪回転使用のものであるため、シールリップ５２、５３を内輪２１に弾性接触させるようにしたが、外輪回転使用の深みぞ玉軸受においては、シールリップ５２、５３を外輪１１に弾性接触させるようにする。   In the embodiment, since the deep groove ball bearing is for inner ring rotation, the seal lips 52 and 53 are elastically brought into contact with the inner ring 21. However, in the deep groove ball bearing for outer ring rotation, the seal lip 52 is used. , 53 are brought into elastic contact with the outer ring 11.

１１ 外輪（外方軌道輪）
１２ 軌道溝
１３ａ 肩
１３ｂ 肩
２１ 内輪（内方軌道輪）
２２ 軌道溝
２３ａ 肩
２３ｂ 肩
２４ シール溝
２５ 内壁面
２６ 円筒面（円筒状周面）
２７ 肩外径面（円筒状周面）
３１ ボール
４０ 保持器
５０ シール部材
５２ 内向きシールリップ
５３ 外向きシールリップ
６０ ヘリカルギヤ
６１ シャフト
Ａ 深みぞ玉軸受 11 Outer ring (outer raceway ring)
12 raceway groove 13a shoulder 13b shoulder 21 inner ring (inner raceway)
22 Track groove 23a Shoulder 23b Shoulder 24 Seal groove 25 Inner wall surface 26 Cylindrical surface (cylindrical peripheral surface)
27 Shoulder outer diameter surface (cylindrical peripheral surface)
31 Ball 40 Cage 50 Seal member 52 Inward seal lip 53 Outward seal lip 60 Helical gear 61 Shaft A Deep groove ball bearing

Claims (4)

内径面に軌道溝を有する外方軌道輪と、外径面に軌道溝を有する内方軌道輪と、外方軌道輪の軌道溝と内方軌道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、前記外方軌道輪における軌道溝の一側の肩と前記内方軌道輪における軌道溝の他側の肩の少なくとも一方の肩の高さを、外方軌道輪の他側の肩と前記内方軌道輪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、前記外方軌道輪と内方軌道輪の一方が固定側とされ、他方が回転側として使用される深みぞ玉軸受において、
前記外方軌道輪と前記内方軌道輪の対向面間に形成された軸受空間の両端開口部内にシール部材を組込んで固定側の軌道輪で支持し、そのシール部材には回転側の軌道輪に弾性接触して軸受空間の両端開口を密閉するシールリップを設け、そのシールリップの少なくとも先端部を、回転側の軌道輪との接触により摩耗して非接触となるか、または、接触圧が零とみなせる程度の軽接触となる高摩耗材で形成し、前記シールリップが、回転側軌道輪の円筒状周面に弾性接触するラジアル接触とされたことを特徴とする深みぞ玉軸受。 An outer race having a raceway groove on the inner diameter surface, an inner race having a raceway groove on the outer diameter surface, a ball incorporated between the raceway groove of the outer raceway and the raceway groove of the inner raceway, A retainer for holding the ball, and the height of at least one of the shoulder on one side of the raceway groove on the outer raceway and the shoulder on the other side of the raceway groove on the inner raceway is set to the outer side. When the height of the shoulder on the other side of the raceway and the shoulder on one side of the inner raceway is higher, the shoulder height of the higher shoulder is H1, and the ball diameter is d, the ball ball The ratio H1 / d of the shoulder height H1 to the diameter d is in the range of 0.25 to 0.50, and one of the outer race ring and the inner race ring is used as the fixed side, and the other is used as the rotation side. In deep groove ball bearings,
A seal member is incorporated into both end openings of a bearing space formed between the opposing surfaces of the outer race ring and the inner race ring, and is supported by a fixed race ring. A seal lip that elastically contacts the ring and seals both end openings of the bearing space is provided, and at least the tip of the seal lip is worn out by contact with the raceway on the rotating side and becomes non-contact or contact pressure A deep groove ball bearing, characterized in that it is made of a high wear material that is light contact that can be regarded as zero, and the seal lip is a radial contact that elastically contacts the cylindrical peripheral surface of the rotating raceway . 前記高摩耗材が、ゴムからなる請求項１に記載の深みぞ玉軸受。   The deep groove ball bearing according to claim 1, wherein the high wear material is made of rubber. 前記高摩耗材が、合成樹脂からなる請求項１に記載の深みぞ玉軸受。   The deep groove ball bearing according to claim 1, wherein the high wear material is made of a synthetic resin. 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１乃至３のいずれかの項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, wherein the pair of rolling bearings comprises the deep groove ball bearing according to any one of claims 1 to 3 .
JP2012006915A 2012-01-17 2012-01-17 Deep groove ball bearing and bearing device Expired - Fee Related JP6050000B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2012006915A JP6050000B2 (en) 2012-01-17 2012-01-17 Deep groove ball bearing and bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2012006915A JP6050000B2 (en) 2012-01-17 2012-01-17 Deep groove ball bearing and bearing device

Publications (2)

Publication Number Publication Date
JP2013148115A JP2013148115A (en) 2013-08-01
JP6050000B2 true JP6050000B2 (en) 2016-12-21

Family

ID=49045806

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2012006915A Expired - Fee Related JP6050000B2 (en) 2012-01-17 2012-01-17 Deep groove ball bearing and bearing device

Country Status (1)

Country Link
JP (1) JP6050000B2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103742543B (en) * 2013-12-18 2017-01-18 宁波摩盛轴承有限公司 Bearing seal device
JP2015132288A (en) * 2014-01-10 2015-07-23 Ntn株式会社 Ball bearing

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2566748Y2 (en) * 1992-01-31 1998-03-30 日本精工株式会社 Sealed deep groove ball bearings for cell motors
JP2000145795A (en) * 1998-11-06 2000-05-26 Ntn Corp Deep groove ball bearing
JP2003287040A (en) * 2002-03-28 2003-10-10 Nsk Ltd Rolling bearing with sealing seal
JP2004211862A (en) * 2003-01-08 2004-07-29 Koyo Seiko Co Ltd Pulley supporting device
JP5455334B2 (en) * 2008-07-09 2014-03-26 Ｎｔｎ株式会社 Sealed bearing
JP2011007288A (en) * 2009-06-26 2011-01-13 Ntn Corp Deep groove ball bearing and gear support device
JP2011127702A (en) * 2009-12-18 2011-06-30 Ntn Corp Rolling bearing
JP2011163395A (en) * 2010-02-05 2011-08-25 Toyota Motor Corp Oil supply device

Also Published As

Publication number Publication date
JP2013148115A (en) 2013-08-01

Similar Documents

Publication Publication Date Title
JP5870563B2 (en) Roller bearing cage and rolling bearing
WO2010150707A1 (en) Synthetic resin holder for deep groove ball bearings, deep groove ball bearing, and gear supporting device
JP2007032612A (en) Roller bearing
JP2014231856A (en) Rolling bearing
JP2012041940A (en) Retainer of cylindrical roller bearing and cylindrical roller bearing
JP6234137B2 (en) Deep groove ball bearing
JP2010019296A (en) Bearing with seal
JP6050000B2 (en) Deep groove ball bearing and bearing device
JP2020041659A (en) Ball bearing
JP2017190874A (en) Deep groove ball bearing and bearing device
JP2008261478A (en) Radial ball bearing cage and radial ball bearing
JP2013092241A (en) Deep groove ball bearing and bearing device
JP6267851B2 (en) Deep groove ball bearing and bearing device
JP5376310B2 (en) Synthetic resin cage and deep groove ball bearing for deep groove ball bearings
JP6537297B2 (en) Deep groove ball bearings
JP2005003198A (en) Rolling bearing and transmission for hybrid car or fuel cell car using the same
JP2013072451A (en) Deep groove ball bearing and bearing device
WO2013012357A1 (en) Bearing unit
JPH10274243A (en) Rolling bearing device equipped with oil supplying means
JP5050910B2 (en) Ball bearing cage and ball bearing
JP2009168171A (en) Roller bearing
JP5012383B2 (en) Radial roller bearing with cage
JP2011196393A (en) Thrust roller bearing
JP2009092158A (en) Rolling bearing
JP5012500B2 (en) Deep groove ball bearing

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20141104

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20150818

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20150820

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20151015

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20160329

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20160530

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20161108

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20161124

R150 Certificate of patent or registration of utility model

Ref document number: 6050000

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees