JP5471265B2 - Rolling bearing with seal ring - Google Patents

Rolling bearing with seal ring Download PDF

Info

Publication number
JP5471265B2
JP5471265B2 JP2009233002A JP2009233002A JP5471265B2 JP 5471265 B2 JP5471265 B2 JP 5471265B2 JP 2009233002 A JP2009233002 A JP 2009233002A JP 2009233002 A JP2009233002 A JP 2009233002A JP 5471265 B2 JP5471265 B2 JP 5471265B2
Authority
JP
Japan
Prior art keywords
ring
head
seal
seal ring
thickness
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
JP2009233002A
Other languages
Japanese (ja)
Other versions
JP2011080527A (en
Inventor
貴美子 中井
幸治 早坂
謹次 湯川
陽一 今村
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.)
NSK Ltd
Original Assignee
NSK Ltd
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 NSK Ltd filed Critical NSK Ltd
Priority to JP2009233002A priority Critical patent/JP5471265B2/en
Publication of JP2011080527A publication Critical patent/JP2011080527A/en
Application granted granted Critical
Publication of JP5471265B2 publication Critical patent/JP5471265B2/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
    • F16C33/7816—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
    • 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
    • F16C33/7856—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 with a single sealing lip
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/60—Thickness, e.g. thickness of coatings

Landscapes

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

Description

この発明は、自動車用変速機等、各種回転装置の回転支持部に組み込んだ状態で、回転軸等の回転部材を、ハウジング等の固定部分に回転自在に支持する為に利用する転がり軸受の開口部を塞ぐシールリングを組み込んだ転がり軸受の改良に関する。 The present invention relates to an opening of a rolling bearing that is used to rotatably support a rotating member such as a rotating shaft on a fixed part such as a housing in a state where the rotating member is incorporated in a rotating support portion of various rotating devices such as an automobile transmission. The present invention relates to an improvement of a rolling bearing incorporating a seal ring that closes a portion.

各種回転支持部に組み込む為の軸受として、玉軸受、ころ軸受、円すいころ軸受等の、各種転がり軸受が広く使用されている。又、この様な転がり軸受として、端部開口をシールリングにより塞いだ、シールリング付転がり軸受も、例えば特許文献１〜４に記載される等により、従来から広く知られている。図５〜６は、このうちの特許文献３に記載された、シールリング付転がり軸受の従来構造の１例として、シールリング付の単列深溝型玉軸受を示している。先ず、この従来構造に就いて説明する。   Various types of rolling bearings such as ball bearings, roller bearings, and tapered roller bearings are widely used as bearings to be incorporated into various rotation support portions. As such a rolling bearing, a rolling bearing with a seal ring in which an end opening is closed with a seal ring has been widely known, for example, as described in Patent Documents 1 to 4. 5 to 6 show a single-row deep groove ball bearing with a seal ring as an example of a conventional structure of a rolling bearing with a seal ring described in Patent Document 3 among them. First, this conventional structure will be described.

外輪１の内周面中央部に形成した深溝型の外輪軌道２と、内輪３の外周面中央部に形成した深溝型の内輪軌道４との間に、それぞれが転動体である複数個の玉５を、保持器６で保持した状態で、転動自在に設ける事により、前記外輪１と前記内輪３とを、同心に、且つ、相対回転を自在に組み合わせている。又、これら外輪１の内周面と内輪３の外周面との間に存在し、前記各玉５を配置した軸受内部空間７の両端開口部を、それぞれ円輪状のシールリング８、８により塞いでいる。   A plurality of balls, each of which is a rolling element, between a deep groove type outer ring raceway 2 formed at the center of the inner peripheral surface of the outer ring 1 and a deep groove type inner ring raceway 4 formed at the center of the outer peripheral surface of the inner ring 3. The outer ring 1 and the inner ring 3 are concentrically and freely combined with each other so as to freely rotate. Further, both end openings of the bearing internal space 7 which are present between the inner peripheral surface of the outer ring 1 and the outer peripheral surface of the inner ring 3 and in which the balls 5 are arranged are respectively closed by annular seal rings 8 and 8. It is out.

これら両シールリング８、８はそれぞれ、芯金９と弾性材１０とを備える。このうちの芯金９は、鋼板等の金属板に、打ち抜き、曲げ等のプレス加工を施す事により、全体を円輪状としている。又、前記弾性材１０は、ゴムの如きエラストマー製で、前記芯金９を包埋した状態で円輪状に成形されて、この芯金９により補強されている。又、前記弾性材１０の内外両周縁部のうちの外周縁部は、この芯金９の外周縁よりも径方向外方に少し突出させて、弾性係止部１１としている。これに対して、前記弾性材１０の内周縁部は、前記芯金９の内周縁よりも径方向内方に十分に突出させて、シールリップ１２としている。このシールリップ１２は、前記芯金９の内周縁寄り部分に存在する薄肉部１３と、この薄肉部１３を挟んでこの芯金９と反対側である内周縁部に存在する、この薄肉部１３よりも厚肉の頭部１４とを備える。尚、前記特許文献３に記載された構造の場合には、この薄肉部１３の内側片面に、土手状の流体膜発生部を形成しているが、この様な構造を持たない薄肉部の形状に就いては、例えば特許文献１に記載されている。   Each of these seal rings 8 and 8 includes a cored bar 9 and an elastic material 10. Of these, the metal core 9 is formed into an annular shape by subjecting a metal plate such as a steel plate to press working such as punching and bending. The elastic member 10 is made of an elastomer such as rubber, and is molded into an annular shape with the core 9 embedded therein, and is reinforced by the core 9. The outer peripheral edge portion of the inner and outer peripheral edge portions of the elastic member 10 protrudes slightly outward in the radial direction from the outer peripheral edge of the core metal 9 to form an elastic locking portion 11. On the other hand, the inner peripheral edge of the elastic member 10 is sufficiently protruded radially inward from the inner peripheral edge of the core 9 to form a seal lip 12. The seal lip 12 has a thin portion 13 that is present near the inner peripheral edge of the metal core 9 and a thin portion 13 that is present on the inner peripheral edge opposite to the metal core 9 with the thin portion 13 in between. And a thicker head 14. In the case of the structure described in Patent Document 3, a bank-like fluid film generating part is formed on one inner surface of the thin part 13, but the shape of the thin part not having such a structure. For example, it is described in Patent Document 1.

上述の様なシールリング８、８を装着すべく、前記外輪１の内周面両端部に係止溝１５、１５を、それぞれ全周に亙って形成している。又、前記内輪３の外周面両端部に凹溝１６、１６を、それぞれ全周に亙って形成している。前記両シールリング８、８は、それぞれの外周縁部に設けた弾性係止部１１を前記両係止溝１５、１５に係止すると共に、前記頭部１４を前記両凹溝１６、１６内に進入させ、この頭部１４の内側縁をこれら両凹溝１６、１６の内側面に全周に亙り摺接させた状態に組み立てる。この状態で、前記軸受内部空間７を、外部空間から遮断する。この様なシールリング付転がり軸受を、例えば自動車用変速機のケーシング内に設けた回転支持部に組み込んだ状態で、前記両シールリング８、８は、変速用のギヤの噛み合い部等で発生した摩耗粉等の異物が、前記軸受内部空間７内に入り込む事を防止する。そして、この異物により、前記外輪軌道２及び前記内輪軌道４と前記各玉５の転動面との転がり接触部が損傷する事を防止する。   In order to mount the seal rings 8 and 8 as described above, locking grooves 15 and 15 are formed on both ends of the inner peripheral surface of the outer ring 1 over the entire circumference. In addition, concave grooves 16 and 16 are formed on both ends of the outer peripheral surface of the inner ring 3 over the entire circumference. Both the seal rings 8, 8 lock the elastic locking portions 11 provided on the outer peripheral edge portions of the seal rings 8, 8 to the locking grooves 15, 15, and the head 14 is inserted into the concave grooves 16, 16. And the inner edge of the head 14 is assembled in a state in which the inner edge of the head 14 is in sliding contact with the inner side surfaces of the concave grooves 16 and 16 over the entire circumference. In this state, the bearing internal space 7 is blocked from the external space. In a state in which such a rolling bearing with a seal ring is incorporated in, for example, a rotation support portion provided in a casing of an automobile transmission, both the seal rings 8 and 8 are generated at a meshing portion of a gear for shifting. Foreign matter such as wear powder is prevented from entering the bearing internal space 7. The foreign matter prevents the rolling contact portion between the outer ring raceway 2 and the inner ring raceway 4 and the rolling surface of each ball 5 from being damaged.

ところで、近年に於ける省エネルギ化の流れにより、シールリング付転がり軸受の回転抵抗（動トルク）を低く抑える要求が強くなっている。一方、シールリング付転がり軸受の回転抵抗に前記両シールリング８、８の摩擦抵抗が占める割合は相当に大きい。従って、この回転抵抗を低減する為には、この摩擦抵抗を低減する事が効果がある。又、この摩擦抵抗を低くする為には、前記頭部１４の内側縁が前記凹溝１６の内側面に押し付けられる力を低く抑える事が効果がある。更に、この力を低く抑える為には、前記薄肉部１３の厚さを小さくして、この薄肉部１３の剛性を低く抑える事が効果がある。   By the way, with the trend of energy saving in recent years, there is an increasing demand for keeping the rotational resistance (dynamic torque) of a rolling bearing with a seal ring low. On the other hand, the ratio of the frictional resistance of the seal rings 8 and 8 to the rotational resistance of the rolling bearing with seal ring is considerably large. Therefore, in order to reduce this rotational resistance, it is effective to reduce this frictional resistance. In order to reduce the frictional resistance, it is effective to reduce the force with which the inner edge of the head 14 is pressed against the inner surface of the concave groove 16. Furthermore, in order to keep this force low, it is effective to reduce the thickness of the thin portion 13 and keep the rigidity of the thin portion 13 low.

但し、単に前記厚さを小さくしただけでは、この薄肉部１３の剛性が徒に低下し、前記頭部１４の内側縁と前記凹溝１６の内側面との摺動部が不安定になる。即ち、単に前記薄肉部１３の厚さを小さくすると、この薄肉部１３の剛性が、あらゆる方向に関して低くなり、前記頭部１４が、前記シールリング８、８の厚さ方向（前記シールリング付転がり軸受の軸方向）だけでなく、径方向にも変位し易くなる。この状態では、前記摺動部の状態が不安定に（摺動部が周囲に振れ動き易く）なり、この摺動部のシール性確保が難しくなる。具体的には、シールリング付転がり軸受の周囲に存在する異物が、この摺動部を通過して、前記軸受内部空間７内に入り込み易くなる。 However, if the thickness is simply reduced , the rigidity of the thin-walled portion 13 is reduced, and the sliding portion between the inner edge of the head 14 and the inner surface of the groove 16 becomes unstable. That is, if the thickness of the thin portion 13 is simply reduced, the rigidity of the thin portion 13 is reduced in all directions, and the head 14 is moved in the thickness direction of the seal rings 8 and 8 (rolling with the seal ring). It becomes easy to displace not only in the axial direction of the bearing) but also in the radial direction. In this state, the state of the sliding portion becomes unstable (the sliding portion easily swings around), and it becomes difficult to ensure the sealing property of the sliding portion. Specifically, foreign matters existing around the rolling bearing with a seal ring easily pass through the sliding portion and enter the bearing internal space 7.

更には、単に前記薄肉部１３の厚さを小さくしただけの場合には、前記弾性材１０の形状精度及び寸法精度の確保が難しくなるだけでなく、この弾性材１０の成形時に、前記薄肉部１３に欠肉等の欠陥を生じ易くなり、歩留まりの悪化により、シールリング８、８の製造コストが嵩む。即ち、前記弾性材１０は、ゴム材料を金型のキャビティ内に送り込む成形により造るが、前記厚さを単に小さくしただけの場合には、この弾性材１０の形状精度及び寸法精度を確保しにくくなるだけでなく、前記成形時に前記キャビティ内に前記ゴム材料が行き渡りにくくなって、前記欠陥を生じ易くなる。 Furthermore, when the thickness of the thin portion 13 is simply reduced, not only is it difficult to ensure the shape accuracy and dimensional accuracy of the elastic material 10, but also when the elastic material 10 is molded, the thin portion It becomes easy to produce defects, such as lacking in 13, and the manufacturing cost of the seal rings 8 and 8 increases due to the deterioration of the yield. That is, the elastic member 10, the rubber material made more molding fed into the mold cavity, but in the case of mere reduced the thickness to ensure the shape accuracy and the dimensional accuracy of the elastic member 10 Not only becomes difficult, but also the rubber material is difficult to spread in the cavity at the time of molding, and the defect is likely to occur.

特許文献２、４には、シールリップの断面形状を工夫する事により、当該シールリップの先端縁と相手面との摺接部のシール性向上を図る発明が記載されている。前記特許文献２、４に記載された発明の構造は、何れも、シールリップの基端部の肉厚を小さくして、当該シールリップの先端縁の相手面に対する追従性を向上させている。但し、前記特許文献２、４に記載された発明の場合には、何れも、基端部以外の部分の厚さ寸法が十分に大きいとは言えないものであり、この基端部以外の部分も或る程度弾性変形する。この為、シールリップの先端縁と相手面との摺動部の状態を必ずしも安定させられず、例えば自動車用変速機の回転支持部に組み込んだ場合に、十分なシール性を確保できない可能性がある。   Patent Documents 2 and 4 describe inventions that improve the sealing performance of the sliding contact portion between the tip edge of the seal lip and the mating surface by devising the cross-sectional shape of the seal lip. In each of the structures of the inventions described in Patent Documents 2 and 4, the thickness of the base end portion of the seal lip is reduced, and the followability of the tip edge of the seal lip to the mating surface is improved. However, in the case of the inventions described in Patent Documents 2 and 4, it cannot be said that the thickness dimension of the portion other than the base end is sufficiently large. Is also elastically deformed to some extent. For this reason, the state of the sliding portion between the tip edge of the seal lip and the mating surface cannot always be stabilized, and there is a possibility that sufficient sealing performance cannot be ensured, for example, when incorporated in the rotation support portion of an automobile transmission. is there.

本発明は、上述の様な事情に鑑みて、回転抵抗が低く、しかも、シールリップの先端面と相手面との摺動状態を安定させて十分にシール性能を確保できるシールリング付転がり軸受を、シールリングの歩留まりを悪化させる事なく実現すべく発明したものである。   In view of the circumstances as described above, the present invention provides a rolling bearing with a seal ring that has a low rotational resistance and that can stabilize the sliding state between the tip surface of the seal lip and the mating surface to ensure sufficient sealing performance. The invention was invented to realize the seal ring without deteriorating the yield.

本発明のシールリング付転がり軸受は、前述した従来から知られているシールリング付転がり軸受と同様に、内周面に外輪軌道を有する外輪と、外周面に内輪軌道を有する内輪と、これら外輪軌道と内輪軌道との間に転動自在に設けられた複数個の転動体と、前記外輪の内周面と前記内輪の外周面との間に存在してこれら各転動体を設置した空間の端部開口を塞ぐシールリングとを備える。
このうちのシールリングは、前述した従来から知られている転がり軸受用シールリングと同様に、円輪状の芯金と、この芯金により補強された円輪状の弾性材とを備える。そして、この弾性材の内外両周縁部のうちの内周縁部を、前記芯金の内周縁よりも径方向内方に突出させると共に、突出した部分をシールリップとしている。このシールリップは、前記芯金の内周縁寄り部分に存在する薄肉部と、この薄肉部を挟んでこの芯金と反対側の端縁部に存在する、この薄肉部よりも厚肉の頭部とを備える。
特に、本発明の場合には、この薄肉部の厚さが、この頭部から遠い基端側で最も小さく、この頭部に近い先端側に向かうほど漸次大きくなっている。
更に、前記シールリングの外周縁部を、前記外輪の端部内周面に形成された係止溝に係止固定する。又、このシールリングの内周縁部に設けられた前記シールリップの頭部のうちで少なくとも軸方向の厚さが最も大きくなった部分を、前記内輪の端部外周面に設けられた凹溝内に、全周に亙って進入させる。そして、前記外輪及びこの内輪の軸方向に関して、前記頭部の一側縁を前記凹溝の片側内面に、全周に亙って軸方向に摺接させ、同じくこの頭部の他側縁をこの凹溝の他側内面に、全周に亙って近接対向させて、当該部分にラビリンスシールを形成している。 The rolling bearing with a seal ring of the present invention includes an outer ring having an outer ring raceway on an inner peripheral surface, an inner ring having an inner ring raceway on an outer peripheral surface, and these outer rings, similarly to the conventionally known rolling bearing with a seal ring. A plurality of rolling elements provided between the raceway and the inner ring raceway so as to be freely rollable, and a space between the inner circumference surface of the outer ring and the outer circumference surface of the inner ring, in which the respective rolling elements are installed. And a seal ring for closing the end opening.
Among these, the seal ring includes a ring- shaped cored bar and a ring-shaped elastic material reinforced by the cored bar, like the conventionally known rolling bearing seal ring. And the inner peripheral edge part of the inner and outer peripheral edge parts of this elastic material protrudes radially inward from the inner peripheral edge of the core metal, and the protruding part is used as a seal lip. The seal lip has a thin wall portion located near the inner peripheral edge of the core bar, and a head portion thicker than the thin wall section, which is present at an end edge opposite to the core bar with the thin wall portion interposed therebetween. With.
Particularly, in the case of the present invention, the thickness of the thin portion, the smallest distant base end side from the head, which is gradually larger as toward the tip end closer to the head.
Further, the outer peripheral edge of the seal ring is locked and fixed in a locking groove formed on the inner peripheral surface of the end of the outer ring. Further, at least a portion of the head portion of the seal lip provided at the inner peripheral edge portion of the seal ring having the largest thickness in the axial direction is placed in the recessed groove provided on the outer peripheral surface of the end portion of the inner ring. Next, let it go all around. Then, with respect to the axial direction of the outer ring and the inner ring, one side edge of the head is brought into sliding contact with the inner surface on one side of the concave groove in the axial direction over the entire circumference, and the other side edge of the head is also formed. A labyrinth seal is formed on the inner surface of the other side of the concave groove so as to face and oppose the entire circumference.

この様な請求項１に記載したシールリング付転がり軸受の発明を実施する場合に好ましくは、請求項２に記載した発明の様に、前記頭部の厚さを、前記薄肉部の平均厚さの２倍以上５倍以下とする。 When carrying out the invention of the rolling bearing with seal ring described in claim 1 , it is preferable that the thickness of the head is set to the average thickness of the thin portion as in the invention described in claim 2. 2 times or more and 5 times or less.

上述の様に構成する本発明によれば、回転抵抗が低く、しかも、シールリップの先端縁と相手面との摺動状態を安定させて十分にシール性能を確保できるシールリング付転がり軸受を、シールリングの歩留まりを悪化させる事なく実現できる。
即ち、シールリップを構成する薄肉部の径方向の一部に、他の部分よりも厚さが小さい部分を設けている為、このシールリップを弾性変形し易くして、摺動トルクを低く抑えられる。更に、薄肉部の厚さを、基端側で小さく、先端側で大きくしている為、頭部が揺動変位する際の中心（支点）から摺接部（作用点）までの距離を長く確保できて、前記シールリップを弾性変形させるモーメントを大きくでき、この面からも摺動トルクを低く抑えられる。従って、シールリング付転がり軸受の回転抵抗を低く抑えられる。
又、シールリップを構成する薄肉部の厚さを、基端側で小さく、先端側で大きくしている為、このシールリップの先端に設けた頭部が、前記薄肉部の基端側部分を中心に揺動変位する。そして、前記頭部が揺動変位する際の半径が大きく（これら基端側部分から頭部までの距離に）なり、この揺動変位に伴う、この頭部の径方向の変位量を小さく抑えられる。又、前記薄肉部の剛性が、前記基端側部分を除いて或る程度大きくなる為、この薄肉部のうちでこの基端側部分以外の部分の弾性変形が抑えられ、この面からも、前記頭部の径方向の変位を抑えられる。更に、揺動変位に伴う、シールリップの接触角の角度変動も小さく抑えられる。従って、シールリップの先端面と相手面との摺動状態を安定させる事ができて、十分にシール性能を確保できる。
しかも、前記薄肉部の厚さは、前記基端側部分を除いて或る程度大きい為、この薄肉部を含む弾性材の成形時に、この弾性材の形状精度及び寸法精度を確保し易くなるだけでなく、前記薄肉部に欠肉等の欠陥を生じにくくして、歩留まりを確保できる。この為、シールリング付転がり軸受の製造コストを抑えられる。 According to the present invention configured as described above, a rolling bearing with a seal ring that has a low rotational resistance and that can stabilize the sliding state between the tip edge of the seal lip and the mating surface to ensure sufficient sealing performance, This can be realized without deteriorating the yield of the seal ring.
That is, since a portion with a smaller thickness than the other portions is provided in a part of the thin portion constituting the seal lip in the radial direction, the seal lip is easily elastically deformed and the sliding torque is kept low. It is done. Furthermore, since the thickness of the thin wall portion is small on the proximal end side and large on the distal end side, the distance from the center (fulcrum) to the sliding contact portion (action point) when the head is oscillating and displaced is increased. The moment for elastically deforming the seal lip can be increased, and the sliding torque can be kept low from this surface. Therefore, the rotational resistance of the rolling bearing with seal ring can be kept low.
In addition, since the thickness of the thin part constituting the seal lip is small on the base end side and large on the tip end side, the head provided at the tip end of the seal lip makes the base end side part of the thin wall part. It swings and displaces to the center. The radius at which the head is oscillated is increased (the distance from the base end portion to the head), and the radial displacement of the head associated with the oscillating displacement is kept small. It is done. In addition, since the rigidity of the thin portion is increased to some extent except for the base end portion, elastic deformation of portions other than the base end portion of the thin portion is suppressed, and also from this surface, The radial displacement of the head can be suppressed. Furthermore, the variation in the contact angle of the seal lip accompanying the swinging displacement can be suppressed to a small value. Therefore, the sliding state between the tip surface of the seal lip and the mating surface can be stabilized, and sufficient sealing performance can be secured.
Moreover, since the thickness of the thin portion is somewhat larger except for the base end portion, it is only easy to ensure the shape accuracy and dimensional accuracy of the elastic material when molding the elastic material including the thin portion. In addition, it is possible to ensure the yield by making it difficult for defects such as lacking in the thin portion. For this reason, the manufacturing cost of a rolling bearing with a seal ring can be suppressed.

本発明の実施の形態の１例を示す、シールリング付転がり軸受の部分断面図。The fragmentary sectional view of the rolling bearing with a seal ring which shows one example of embodiment of this invention. シールリングを取り出した状態で示す、部分拡大断面図。The partial expanded sectional view shown in the state which took out the seal ring. 本発明の作用・効果を説明する為の、本発明の技術的範囲に属する構造を示す部分拡大断面図（Ａ）及び本発明の技術的範囲からは外れる構造を示す部分拡大断面図（Ｂ）。The partial expanded sectional view (A) which shows the structure which belongs to the technical scope of this invention, and the partial enlarged sectional view (B) which shows the structure which remove | deviates from the technical scope of this invention for demonstrating the effect | action and effect of this invention . 同じく、（Ａ）は本発明の技術分野に属する構造に関する、（Ｂ）は本発明の技術的範囲からは外れる構造に関する、それぞれ部分拡大断面図（ａ）及び模式図（ｂ）。Similarly, (A) relates to a structure belonging to the technical field of the present invention, and (B) relates to a structure deviating from the technical scope of the present invention, respectively, a partially enlarged sectional view (a) and a schematic view (b). 従来から知られているシールリング付転がり軸受の１例を示す部分断面図。The fragmentary sectional view which shows an example of the rolling bearing with a seal ring known conventionally. 同じくシールリングを取り出して示す部分断面図。The partial sectional view which takes out and shows a seal ring similarly.

図１〜４により、本発明の実施の形態の１例に就いて説明する。尚、本例の特徴は、回転抵抗の低いシールリング付転がり軸受を、シール性能及びシールリングの歩留まりを悪化させる事なく実現すべく、このシールリングの内周縁部に設けたシールリップ１２ａの形状及び寸法を工夫した点にある。その他の部分の構成及び作用は、前述の図５〜６に示した、従来から知られているシールリング及びシールリング付の単列深溝型の玉軸受と同様であるから、同等部分に関する図示並びに説明は、省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。   1-4, an example of an embodiment of the present invention will be described. The feature of this example is the shape of the seal lip 12a provided on the inner peripheral edge of the seal ring in order to realize a rolling bearing with a seal ring having a low rotational resistance without deteriorating the seal performance and the yield of the seal ring. And it is in the point which devised the dimension. The structure and operation of the other parts are the same as those of the conventionally known seal ring and single row deep groove type ball bearing with seal ring shown in FIGS. The description will be omitted or simplified, and the following description will focus on the features of this example.

本例のシールリング８ａは、円輪状の芯金９ａと、この芯金９ａにより補強された円輪状の弾性材１０ａとを備える。そして、この弾性材１０ａの外周縁部を前記芯金９ａの外周縁よりも径方向外方に少し突出させて弾性係止部１１ａとしている。これに対して、前記弾性材１０ａの内周縁部を、前記芯金９ａの内周縁よりも径方向内方に十分に突出させて、突出した部分を前記シールリップ１２ａとしている。このシールリップ１２ａは、薄肉部１３ａと頭部１４ａとを備える。このうちの薄肉部１３ａは、このシールリップ１２ａのうちで、前記芯金９ａの内周縁寄り部分である、径方向外半部に存在する。これに対して前記頭部１４ａは、前記薄肉部１３ａを挟んで前記芯金９ａと反対側である、径方向内端縁部に存在する。   The seal ring 8a of this example includes a ring-shaped cored bar 9a and a ring-shaped elastic member 10a reinforced by the cored bar 9a. And the outer peripheral edge part of this elastic material 10a is made to protrude a little radially outward from the outer peripheral edge of the said core metal 9a, and it is set as the elastic latching | locking part 11a. On the other hand, the inner peripheral edge portion of the elastic member 10a is sufficiently protruded radially inward from the inner peripheral edge of the core metal 9a, and the protruding portion is used as the seal lip 12a. The seal lip 12a includes a thin portion 13a and a head portion 14a. Of these, the thin portion 13a is present in the radially outer half of the seal lip 12a that is closer to the inner peripheral edge of the core metal 9a. On the other hand, the head 14a is present at the radially inner end edge on the opposite side to the cored bar 9a across the thin portion 13a.

このうちの薄肉部１３ａは、断面形状が楔状であって、厚さが、前記頭部１４ａから遠
い基端側となる外径側端部で最も小さく、この頭部１４ａに近い先端側である内径側端部に向かうほど漸次大きくなる。即ち、前記薄肉部１３ａの厚さは、外径側端部で最も小さく（厚さＴ1 ）、径方向中間部で少し大きく（厚さＴ２ ）、内径側端部で最も大きく（厚さＴ3 ）なっている。又、本例の場合には、前記薄肉部１３ａが、前記シールリング８ａの中心軸に対し直交する仮想平面αに対して、内径側に向かうほど内輪３の軸方向中央部に向かう方向に、角度θ（例えば１０〜３０度程度）だけ傾斜している。
一方、前記頭部１４ａの厚さＴ１４は、前記薄肉部１３ａの平均厚さＴの２倍以上、５倍以下｛Ｔ１４＝（２〜５）Ｔ｝とし、且つ、次述する凹溝１６ａの外側内面に接触しない大きさに規制する事が好ましい。 Of these, the thin-walled portion 13a is wedge-shaped in cross section, and the thickness is the smallest at the outer diameter side end portion that is the base end side far from the head portion 14a, and is the distal end side close to the head portion 14a. It becomes gradually larger toward the inner diameter side end. That is, the thickness of the thin portion 13a is the smallest at the outer diameter side end (thickness T 1 ), slightly larger at the radial intermediate portion (thickness T 2 ), and the largest at the inner diameter side end (thickness). T 3) are made by. In the case of this example, the thin portion 13a is directed toward the central portion in the axial direction of the inner ring 3 toward the inner diameter side with respect to a virtual plane α orthogonal to the central axis of the seal ring 8a. It is inclined by an angle θ (for example, about 10 to 30 degrees).
On the other hand, the thickness T 14 of the head 14a, the two or more times the average thickness T of the thin portion 13a, and 5 times or less {T 14 = (2~5) T }, and is described next groove It is preferable to regulate the size so as not to contact the outer inner surface of 16a.

上述の様なシールリング８ａは、外周縁部に設けた弾性係止部１１ａを外輪１の端部内周面に設けた係止溝１５ａに係止すると共に、前記頭部１４ａを、内輪３の端部外周面に設けた凹溝１６ａ内に、全周に亙って進入させる。この状態で、前記頭部１４ａの内側縁を、この凹溝１６ａのうちの内側内面に全周に亙って軸方向に摺接させると共に、この頭部１４ａの外側縁を、この凹溝１６ａのうちの外側内面に、全周に亙って近接対向させる。又、前記弾性材１０ａの基部１７の一部に前記薄肉部１３ａの外側に隣接して設けた、突条１８の先端縁（内周縁）を、前記内輪３のうちで前記凹溝１６ａの外側に隣接した部分の外周面に、全周に亙って近接対向させている。そして、これら２箇所の近接対向させた部分を、それぞれラビリンスシールとしている。 The seal ring 8a as described above locks the elastic locking portion 11a provided on the outer peripheral edge portion into the locking groove 15a provided on the inner peripheral surface of the end portion of the outer ring 1, and the head portion 14a is connected to the inner ring 3. It is made to approach over the perimeter in the ditch | groove 16a provided in the edge part outer peripheral surface. In this state, the inner edge of the head portion 14a is brought into sliding contact with the inner inner surface of the concave groove 16a in the axial direction over the entire circumference, and the outer edge of the head portion 14a is brought into contact with the concave groove 16a. The outer inner surface of each of them is brought close to and opposed across the entire circumference. In addition, the tip edge (inner peripheral edge) of the ridge 18 provided on a part of the base portion 17 of the elastic member 10a adjacent to the outer side of the thin portion 13a is formed outside the concave groove 16a in the inner ring 3. The outer peripheral surface of the portion adjacent to is closely opposed to the entire periphery. Then, these two portions that are close to each other are used as labyrinth seals.

上述の様に構成する本例の構造によれば、回転抵抗が低く、しかも、前記シールリップ１２ａの先端部に設けた頭部１４ａの内側縁と、前記凹溝１６の内側内面との摺動状態を安定させて十分にシール性能を確保できるシールリング付転がり軸受を、前記シールリング８ａの歩留まりを悪化させる事なく実現できる。先ず、歩留まりを悪化させずに回転抵抗を低く抑えられるのは、前記薄肉部１３ａの断面形状を楔状とする事により図れる。即ち、この薄肉部１３ａの断面形状を楔状とし、径方向の一部に厚さが十分に小さい部分を設ける事により、前記頭部１４ａの内側縁を前記凹溝１６の内側内面に押し付ける力を小さく抑えて、これら内側縁と内側内面との摺接部の摩擦抵抗を低く抑え、前記回転抵抗を低く抑えられる。又、前記薄肉部１３ａの厚さを、基端側で小さく、先端側で大きくしている為、前記頭部１４ａが揺動変位する際の中心（支点）から摺接部（作用点）までの距離を長く確保できて、前記頭部１４ａの内側縁を前記凹溝１６の内側内面に押し付ける力を小さく抑えられる。この為、この面からも前記回転抵抗を低く抑えられる。又、前記薄肉部１３ａの厚さが小さいのは、外径側端部のみで、他の部分の厚さは或る程度大きい為、前記薄肉部１３ａを含む、前記シールリップ１２ａの射出成形を安定して行う事ができて、前記歩留まりの悪化を防止できる。   According to the structure of this example configured as described above, the rotational resistance is low, and the sliding between the inner edge of the head 14a provided at the tip of the seal lip 12a and the inner inner surface of the groove 16 is performed. A rolling bearing with a seal ring that can stabilize the state and sufficiently secure the sealing performance can be realized without deteriorating the yield of the seal ring 8a. First, the rotational resistance can be kept low without deteriorating the yield by making the cross-sectional shape of the thin portion 13a wedge-shaped. That is, the cross-sectional shape of the thin-walled portion 13a is wedge-shaped, and a force that presses the inner edge of the head portion 14a against the inner inner surface of the concave groove 16 is provided by providing a portion having a sufficiently small thickness in a part in the radial direction. The frictional resistance of the sliding contact portion between the inner edge and the inner inner surface is suppressed to a low level, and the rotational resistance can be suppressed to a low level. Further, since the thickness of the thin portion 13a is small on the proximal end side and large on the distal end side, from the center (fulcrum) when the head portion 14a is oscillating and displaced to the sliding contact portion (operation point). Can be secured long, and the force for pressing the inner edge of the head 14a against the inner inner surface of the concave groove 16 can be kept small. For this reason, the rotational resistance can be kept low also from this aspect. Further, the thickness of the thin portion 13a is small only at the outer diameter side end, and the thickness of the other portions is somewhat large. Therefore, the injection molding of the seal lip 12a including the thin portion 13a is performed. This can be performed stably, and the yield can be prevented from deteriorating.

次に、本例の構造によりシール性能を確保できる理由に就いて、図３〜４を参照しつつ説明する。本例の構造の場合には、図３、４の（Ａ）に示す様に、前記シールリップ１２ａを構成する薄肉部１３ａの厚さＴ1 、Ｔ2 、Ｔ3 を、基端側で小さく、先端側で大きくしている（Ｔ1 ＜Ｔ2 ＜Ｔ3 ）。この為、前記シールリップ１２ａの先端に設けた頭部１４ａが、図４の（Ａ）の（ａ）（ｂ）に点Ｏで示した、前記薄肉部１３ａの基端側部分を中心に（この点Ｏを支点とし、前記摺接部を作用点として）揺動変位する。この様に、前記薄肉部１３ａの外径側端部を揺動変位の中心とする場合には、図４の（Ａ）（ｂ）の記載から明らかな通り、前記頭部１４ａが揺動変位する際の半径が大きくなり、この揺動変位に伴う、この頭部１４ａの径方向の変位量δを小さく抑えられる。又、前記薄肉部１３aの剛性が、前記基端側部分を除いて或る程度大きくなる為、この薄肉部１３ａのうちでこの基端側部分以外の部分の弾性変形が抑えられ（この薄肉部１３ａが径方向に関して弾性変形しにくくなり）、この面からも、前記頭部１４ａの径方向の変位を抑えられる。更に、揺動変位に伴う、前記シールリップ１２ａの接触角の角度変動αも小さく抑えられる。そして、この頭部１４ａの内側縁と前記凹溝１６の内側内面との摺動状態を安定させて、前記シールリング８ａによるシール性能の確保を図れる。 Next, the reason why the sealing performance can be ensured by the structure of this example will be described with reference to FIGS. In the case of the structure of this example, as shown in FIGS. 3 and 4A, the thicknesses T 1 , T 2 , T 3 of the thin portion 13a constituting the seal lip 12a are made smaller on the base end side. , Larger at the tip side (T 1 <T 2 <T 3 ). For this reason, the head 14a provided at the distal end of the seal lip 12a is centered on the proximal end portion of the thin portion 13a indicated by the point O in FIGS. Using this point O as a fulcrum, the sliding contact portion is used as a swing point. As described above, when the outer diameter side end of the thin portion 13a is used as the center of the swing displacement, the head portion 14a is swung as shown in FIGS. 4A and 4B. In this case, the radius at which the head 14a is moved is increased, and the displacement δ in the radial direction of the head 14a associated with the swinging displacement can be kept small. Further, since the rigidity of the thin portion 13a is increased to a certain extent except for the base end portion, elastic deformation of portions other than the base end portion of the thin portion 13a is suppressed (this thin portion 13a). 13a is less likely to be elastically deformed in the radial direction), and also from this surface, the radial displacement of the head 14a can be suppressed. Furthermore, the angle variation α of the contact angle of the seal lip 12a accompanying the oscillating displacement can be suppressed to be small. The sliding state between the inner edge of the head portion 14a and the inner inner surface of the concave groove 16 can be stabilized, and the sealing performance by the seal ring 8a can be ensured.

この様な本例の構造に対して、図３、４の（Ｂ）に示す様に、シールリップ１２ｂを構成する薄肉部１３ｂの厚さＴ4 、Ｔ5 、Ｔ6 を、基端側で大きく、先端側で小さくすると（Ｔ4 ＞Ｔ5 ＞Ｔ6 ）、頭部１４ｂが揺動変位する際の半径が小さくなる。そして、この頭部１４ｂの軸方向に関する変位Ｌが、前記図４の（Ａ）と同じである場合でも、前記揺動変位に伴う、前記頭部１４ｂの径方向の変位量△が大きくなる。又、揺動変位に伴う、前記シールリップ１２ｂの接触角の角度変動βも大きくなる。この様な状態では、この頭部１４ｂの内側縁と凹溝１６の内側内面との摺動状態が不安定になり、シールリング８ｂによるシール性能の確保を図りにくくなる。又、前記径方向に関する変位量△が大きくなる分、前記頭部１４ｂの内側縁と前記凹溝１６の内側内面との摺動部の摩擦抵抗が大きくなり、前記シールリング８ｂを組み込んだシールリング付転がり軸受の回転抵抗が大きくなる。 With respect to the structure of this example, as shown in FIGS. 3 and 4B, the thicknesses T 4 , T 5 and T 6 of the thin wall portion 13b constituting the seal lip 12b are set at the proximal end side. If it is large and small on the tip side (T 4 > T 5 > T 6 ), the radius at which the head 14b is displaced is reduced. Even when the displacement L in the axial direction of the head 14b is the same as that shown in FIG. 4A, the radial displacement amount Δ of the head 14b accompanying the oscillating displacement increases. Further, the angle variation β of the contact angle of the seal lip 12b accompanying the oscillating displacement increases. In such a state, the sliding state between the inner edge of the head 14b and the inner inner surface of the groove 16 becomes unstable, and it becomes difficult to ensure the sealing performance by the seal ring 8b. Further, as the displacement amount Δ in the radial direction increases, the frictional resistance of the sliding portion between the inner edge of the head portion 14b and the inner inner surface of the concave groove 16 increases, and the seal ring incorporating the seal ring 8b. The rotational resistance of the rolling bearing increases.

本発明は、自動車用変速機の回転支持部を構成する様な、小型のシールリングを組み込んだシールリング付転がり軸受の改良に関する。従って、転がり軸受としては、小型の玉軸受が主となるが、ころ軸受、円すいころ軸受等、他の型式の転がり軸受への適用を排除するものではない。更に、例えば外輪回転型の転がり軸受で実施する場合に、シールリングの形状を、径方向に関して、内外逆にする事もできる。 The present invention relates to an improvement in a rolling bearing with a seal ring incorporating a small seal ring , which constitutes a rotation support portion of a transmission for an automobile. Therefore, although small ball bearings are mainly used as rolling bearings, application to other types of rolling bearings such as roller bearings and tapered roller bearings is not excluded. Further, for example, in the case of an outer ring rotating type rolling bearing, the shape of the seal ring can be reversed in the radial direction.

１ 外輪
２ 外輪軌道
３ 内輪
４ 内輪軌道
５ 玉
６ 保持器
７ 軸受内部空間
８、８ａ、８ｂ シールリング
９、９ａ 芯金
１０、１０ａ 弾性材
１１、１１ａ 弾性係止部
１２、１２ａ、１２ｂ シールリップ
１３、１３ａ、１３ｂ 薄肉部
１４、１４ａ、１４ｂ 頭部
１５、１５ａ 係止溝
１６、１６ａ 凹溝
１７ 基部
１８ 突条 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Outer ring raceway 3 Inner ring 4 Inner ring raceway 5 Ball 6 Cage 7 Bearing inner space 8, 8a, 8b Seal ring 9, 9a Core metal 10, 10a Elastic material 11, 11a Elastic locking part 12, 12a, 12b Seal lip 13, 13a, 13b Thin portion 14, 14a, 14b Head portion 15, 15a Locking groove 16, 16a Recessed groove 17 Base 18 Projection

特開平１０−３３９３２９号公報JP 10-339329 A 特開２００４−１００８４２号公報JP 2004-1000084 A 特開２００４−２５７４２１号公報JP 2004-257421 A 国際公開ＷＯ２００３／０８１０９６号公報International Publication WO2003 / 081096

Claims (2)

内周面に外輪軌道を有する外輪と、外周面に内輪軌道を有する内輪と、これら外輪軌道と内輪軌道との間に転動自在に設けられた複数個の転動体と、前記外輪の内周面と前記内輪の外周面との間に存在してこれら各転動体を設置した空間の端部開口を塞ぐシールリングとを備えたシールリング付転がり軸受に於いて、
前記シールリングが、円輪状の芯金と、この芯金により補強された円輪状の弾性材とを備え、この弾性材の内外両周縁部のうちの内周縁部を、前記芯金の内周縁よりも径方向内方に突出させると共に、突出した部分を、この芯金の内周縁寄り部分に存在する薄肉部と、この薄肉部を挟んでこの芯金と反対側の端縁部に存在する、この薄肉部よりも厚肉の頭部とを備え、このうちの薄肉部の厚さが、この頭部から遠い基端側で最も小さく、この頭部に近い先端側に向かうほど漸次大きくなっているシールリップとしており、
前記シールリングの外周縁部が、前記外輪の端部内周面に形成された係止溝に係止固定されており、このシールリングの内周縁部に設けられた前記シールリップの頭部のうちで少なくとも軸方向の厚さが最も大きくなった部分が、前記内輪の端部外周面に設けられた凹溝内に、全周に亙って進入しており、前記外輪及びこの内輪の軸方向に関して、前記頭部の一側縁が前記凹溝の片側内面に、全周に亙って軸方向に摺接しており、同じくこの頭部の他側縁がこの凹溝の他側内面に、全周に亙って近接対向して、当該部分にラビリンスシールを形成している
事を特徴とするシールリング付転がり軸受。 An outer ring having an outer ring raceway on an inner peripheral surface, an inner ring having an inner ring raceway on an outer peripheral surface, a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway, and an inner circumference of the outer ring In a rolling bearing with a seal ring, including a seal ring that exists between a surface and an outer peripheral surface of the inner ring and closes an end opening of a space in which each of the rolling elements is installed,
The seal ring includes a ring- shaped cored bar and a ring-shaped elastic material reinforced by the cored bar, and the inner peripheral edge of the inner and outer peripheral edges of the elastic material is the inner peripheral edge of the cored bar. The protruding portion is present in the radially inward direction, and the protruding portion is present at a portion near the inner peripheral edge of the core metal, and at the edge portion on the opposite side of the core metal with the thin portion interposed therebetween. , and a head portion having a thickness thicker than the thin portion, the thickness of the thin portion of this is the smallest, gradually becomes larger as toward the tip end closer to the head from the head distant base end It has a sealing lip that
The outer peripheral edge of the seal ring is locked and fixed in a locking groove formed on the inner peripheral surface of the end of the outer ring, and the head of the seal lip provided on the inner peripheral edge of the seal ring And at least the portion with the largest axial thickness has entered the entire groove in the groove provided on the outer peripheral surface of the end of the inner ring, and the axial direction of the outer ring and the inner ring. The one side edge of the head is in sliding contact with the inner surface on one side of the groove, and the other side edge of the head is also on the other surface of the groove. A rolling bearing with a seal ring, characterized in that a labyrinth seal is formed in the part in close proximity over the entire circumference . 前記頭部の厚さが、前記薄肉部の平均厚さの２倍以上５倍以下である、請求項１に記載したシールリング付転がり軸受。The rolling bearing with a seal ring according to claim 1, wherein the thickness of the head is 2 to 5 times the average thickness of the thin portion.
JP2009233002A 2009-10-07 2009-10-07 Rolling bearing with seal ring Expired - Fee Related JP5471265B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2009233002A JP5471265B2 (en) 2009-10-07 2009-10-07 Rolling bearing with seal ring

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009233002A JP5471265B2 (en) 2009-10-07 2009-10-07 Rolling bearing with seal ring

Publications (2)

Publication Number Publication Date
JP2011080527A JP2011080527A (en) 2011-04-21
JP5471265B2 true JP5471265B2 (en) 2014-04-16

Family

ID=44074785

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2009233002A Expired - Fee Related JP5471265B2 (en) 2009-10-07 2009-10-07 Rolling bearing with seal ring

Country Status (1)

Country Link
JP (1) JP5471265B2 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6331754B2 (en) 2013-07-09 2018-05-30 日本精工株式会社 Ball bearing with seal ring
DE102016209901A1 (en) * 2016-06-06 2017-12-07 Schaeffler Technologies AG & Co. KG Suspension strut bearing and suspension strut with suspension strut bearing
US10458477B2 (en) * 2017-03-28 2019-10-29 Minebea Mitsumi Inc. Seal for rolling bearing and rolling bearing
JP7112201B2 (en) * 2017-03-28 2022-08-03 ミネベアミツミ株式会社 Rolling bearing seals and rolling bearings
CN110307260A (en) * 2019-07-10 2019-10-08 无锡诚石轴承有限公司 Electric tool bearing seal ring assembly
CN115122695B (en) * 2022-07-06 2023-08-25 成都国营锦江机器厂 Rotary shaft lip-shaped sealing ring with elastic element and preparation method thereof

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6165913A (en) * 1984-09-10 1986-04-04 Nippon Seiko Kk Bearing sealing structure
JP4232916B2 (en) * 1997-09-17 2009-03-04 Ｎｔｎ株式会社 Rolling bearing seal structure
JP2008175301A (en) * 2007-01-18 2008-07-31 Nsk Ltd Rolling bearing with sealing device

Also Published As

Publication number Publication date
JP2011080527A (en) 2011-04-21

Similar Documents

Publication Publication Date Title
JP5471265B2 (en) Rolling bearing with seal ring
JP5920443B2 (en) Rolling bearing with seal ring
CN1892061B (en) Sealed rolling bearing
JPH10252762A (en) Sealing device for rolling bearing
JP2017057930A (en) Bearing device for wheel
JP2006266451A (en) Rolling bearing with sealing device
JP2013253689A (en) Oil seal and sealed roller bearing
JP2009063118A (en) Rolling bearing
JP6532651B2 (en) Rolling bearing with seal ring
JP5493667B2 (en) Rolling bearing with seal ring
JP2011144899A (en) Double row rolling bearing
JP6618757B2 (en) Fluid dynamic bearing
JP2016080020A (en) Sealing device
CN201593556U (en) Roller bearing
JP2007333011A (en) Deep groove ball bearing
JP5163461B2 (en) Rolling bearing unit with sensor
JP2009008274A (en) Ball bearing
JP5326358B2 (en) Sealed rolling bearing
JP5581719B2 (en) Thrust roller bearing
JP6981143B2 (en) Ball bearing with seal
KR102075478B1 (en) A Rolling Bearing Having Improved Sealing
JP2003013976A (en) Rolling bearing
JP2006214533A (en) Thrust cylindrical roller bearing
JP2006022867A (en) Rolling bearing with sealing plate
JP2009287626A (en) Rolling bearing device

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20120815

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20130124

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20130514

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20130709

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: 20140107

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20140120

R150 Certificate of patent or registration of utility model

Ref document number: 5471265

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

LAPS Cancellation because of no payment of annual fees